US20190050663A2 - Strapping apparatus - Google Patents
Strapping apparatus Download PDFInfo
- Publication number
- US20190050663A2 US20190050663A2 US15/117,403 US201515117403A US2019050663A2 US 20190050663 A2 US20190050663 A2 US 20190050663A2 US 201515117403 A US201515117403 A US 201515117403A US 2019050663 A2 US2019050663 A2 US 2019050663A2
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- United States
- Prior art keywords
- band
- strapping
- roller
- tensioning
- rollers
- Prior art date
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Images
Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
- B65B—MACHINES, APPARATUS OR DEVICES FOR, OR METHODS OF, PACKAGING ARTICLES OR MATERIALS; UNPACKING
- B65B13/00—Bundling articles
- B65B13/18—Details of, or auxiliary devices used in, bundling machines or bundling tools
- B65B13/22—Means for controlling tension of binding means
-
- G06K9/222—
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
- B65B—MACHINES, APPARATUS OR DEVICES FOR, OR METHODS OF, PACKAGING ARTICLES OR MATERIALS; UNPACKING
- B65B13/00—Bundling articles
- B65B13/02—Applying and securing binding material around articles or groups of articles, e.g. using strings, wires, strips, bands or tapes
- B65B13/04—Applying and securing binding material around articles or groups of articles, e.g. using strings, wires, strips, bands or tapes with means for guiding the binding material around the articles prior to severing from supply
- B65B13/06—Stationary ducts or channels
-
- G06F17/248—
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- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F40/00—Handling natural language data
- G06F40/10—Text processing
- G06F40/166—Editing, e.g. inserting or deleting
- G06F40/186—Templates
-
- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06V—IMAGE OR VIDEO RECOGNITION OR UNDERSTANDING
- G06V30/00—Character recognition; Recognising digital ink; Document-oriented image-based pattern recognition
- G06V30/10—Character recognition
- G06V30/14—Image acquisition
- G06V30/142—Image acquisition using hand-held instruments; Constructional details of the instruments
- G06V30/1423—Image acquisition using hand-held instruments; Constructional details of the instruments the instrument generating sequences of position coordinates corresponding to handwriting
-
- G—PHYSICS
- G09—EDUCATION; CRYPTOGRAPHY; DISPLAY; ADVERTISING; SEALS
- G09G—ARRANGEMENTS OR CIRCUITS FOR CONTROL OF INDICATING DEVICES USING STATIC MEANS TO PRESENT VARIABLE INFORMATION
- G09G5/00—Control arrangements or circuits for visual indicators common to cathode-ray tube indicators and other visual indicators
- G09G5/12—Synchronisation between the display unit and other units, e.g. other display units, video-disc players
-
- G—PHYSICS
- G09—EDUCATION; CRYPTOGRAPHY; DISPLAY; ADVERTISING; SEALS
- G09G—ARRANGEMENTS OR CIRCUITS FOR CONTROL OF INDICATING DEVICES USING STATIC MEANS TO PRESENT VARIABLE INFORMATION
- G09G2354/00—Aspects of interface with display user
-
- H—ELECTRICITY
- H04—ELECTRIC COMMUNICATION TECHNIQUE
- H04W—WIRELESS COMMUNICATION NETWORKS
- H04W88/00—Devices specially adapted for wireless communication networks, e.g. terminals, base stations or access point devices
- H04W88/02—Terminal devices
- H04W88/06—Terminal devices adapted for operation in multiple networks or having at least two operational modes, e.g. multi-mode terminals
Definitions
- the present disclosure relates to a strapping device of a strapping apparatus for the strapping of packaged articles with a strapping band, in particular with a plastics strapping band, which is equipped with an advancement and tensioning device which are equipped with multiple wheels for transmitting an advancement, retraction and tensioning movement to the strapping band, wherein at least one of said wheels is operatively connected or operatively connectable to a drive device to set the at least one of the wheels in rotational motion about an axis of rotation for the advancement, retraction and tensioning movement.
- Strapping apparatuses of said type may be formed as a static installation which is utilized for equipping relatively large packaged articles, or multiple individual packaged articles placed together to form a packaged article unit, with one or more band straps.
- the band straps are normally formed from a band which is drawn from a supply roll and laid as a ring-shaped strap around the packaged article.
- the strapping band is shot with its free end first into a channel of the strapping apparatus, which channel surrounds the packaged article, with a spacing, in the manner of a portal or in ring-shaped fashion. Normally, as soon as the band end has reached a particular point in the channel, the band end is clamped and the band is then retracted again.
- the loop of the strapping band is tightened and the band passes out of the channel and into contact with the packaged article. Subsequently, the band is pulled taut and, in the process, a band tension is applied to the band, and the band ring or the band loop is equipped with a fastening and is cut off from the supply roll.
- strapping band use is made both of metallic bands and of plastics bands.
- the strapping apparatuses are normally adapted to the strapping band types used therewith, in particular with regard to the connecting device by way of which two band layers, which lie one over the other in sections, of the strapping bands can be non-detachably connected to one another.
- the strapping apparatus generally has a band advancement device for the advancement of the strapping band during the formation of a band loop, a band retraction device for the retraction of the strapping band after the formation of the band loop, for the purposes of causing the strapping band to be laid against the packaged article, and a tensioning device, by way of which a band tension in the strapping band laid against the packaged article can be increased, that is to say the band is laid taut against the packaged article.
- These three functional components normally require a multiplicity of components and in particular rollers to impart the individual movements to the band in a functionally reliable manner.
- the strapping device which is normally in the form of a strapping head, is of relatively large construction, and requires a large volume in the strapping apparatus. Furthermore, this results in a high weight of the strapping device.
- the present disclosure is therefore based on the object of improving a strapping apparatus for strapping packaged articles with a strapping band such that the strapping head can be designed to be as compact as possible.
- a strapping device of the type mentioned in the introduction in the case of which, for the contact with the strapping band during the execution and imparting of the advancement, retraction and tensioning movement to the band, a total of at most three rollers are provided on the strapping head, which rollers come into contact with the strapping band in conjunction with said functions, and here, the at most three rollers can, in each case pairwise in different combinations with one another, be placed in contact with the strapping band on both sides of the strapping band.
- the present disclosure can thus also be seen in that, in the case of a strapping device in which it is the case that, for the band handling, that is to say for the action on the strapping band during the generation of the band movements, a band advancement device, a band retraction device and a tensioning device of the strapping device are provided, and here, a roller whose circumferential surface is provided for making contact with the strapping band is a constituent part of the tensioning device and of the band advancement device and of the band retraction device.
- a roller of the strapping device which roller is provided in conjunction with the band movement and for making contact with the strapping band, performs multiple functions and is thus assigned to multiple functional units of the strapping device.
- the tension-relieving process may be realized by way of a motor-driven rotational movement of the tensioning wheel in a direction of rotation of the tensioning wheel which corresponds to the opposite of the direction of rotation provided previously during the tensioning process. Since the band loop that has already been generated can be held in position here by way of suitable clamping means, the tension-relieving process has no influence on the band tension in the band loop.
- the said one roller may advantageously be a counterpart roller which is itself not driven in rotation about its axis of rotation and which is thus freely rotatable about its axis of rotation.
- a position of the said one roller should however advantageously be variable in relation to at least one of the two other rollers by way of a driven movement.
- the said one roller may be attached to a movement device which is driven by motor means or other means, by way of which movement device the movement for the change in position is effected.
- At least one of the three rollers, and in certain embodiments only one of the three rollers should be movable alternately in the direction of in each case one of the two other rollers in order, in a movement end position, to bear together with the in each case one other roller against the band.
- the movable only one roller may thus, as a counterpart roller for two driven rollers, serve primarily for alternately forcing the band against one driven roller and against the other driven roller to reduce or prevent slippage between the band and the driven rollers.
- the movable roller may be provided for performing pivoting movements, in particular driven pivoting movements. Pivoting movements can be generated with particularly little outlay for the purpose of generating the changes in position provided according to the present disclosure.
- Corresponding movement devices and the drive thereof may be realized in a compact construction and integrated, with little space requirement, in a strapping device according to the present disclosure.
- the movement of the movable roller may be in the form of a combined stroke movement and pivoting movement.
- a pure pivoting movement along a radius it is possible in this way to realize either a pivoting movement about a radius with a superposed stroke movement, or else a stroke movement and pivoting movement performed successively in terms of time, by way of which movement it is possible to realize particularly advantageously optimum movement paths and positions of contact of the movable roller against the two further rollers.
- a first roller is formed as a tensioning roller of the tensioning device and a second roller is formed as a roller of the band advancement and band retraction device
- the first and the second roller are operatively connected or operatively connectable to one or more drives for the purposes of generating driven rotational movements of the first and of the second roller
- the third roller which is movable in terms of its position, is arranged so as to be movable in driven fashion between positions of contact with the first and with the second roller.
- the movable roller is thus advantageously movable between two end positions and can be arranged in said two end positions, in which the movable roller is provided for performing either a function of the tensioning device or a function of the band advancement and/or band retraction device.
- a further embodiment of the present disclosure may provide an actuable means by which at least one wheel of a wheel pair of the advancing device can be switched into a state in which the strapping band can be displaced between the wheel pair in a direction opposite to the band advancement movement, without a corresponding motor drive movement being transmitted to the strapping band.
- the state of the wheel pair is changed from a state in which the band is clamped between said wheels, which state permits in particular the advancement of the band, into a state in which the band can move through between the wheel pair regardless of a driven movement of a wheel of the wheel pair.
- the clamping state between the wheel pair which clamping state is provided for the transmission of a motor drive movement via one of the two wheels to the strapping band, is reduced at least to such an extent that slippage or an increased gap can form between the band and the wheel pair. If an enlarged gap between the circumferential surfaces of the wheels is generated in the event of the clamping action being eliminated, said gap should be larger than the band thickness.
- the clamping action may for example be reduced simply by virtue of a pressure force with which the two wheels are pressed against one another being reduced, for example by way of a variably adjustable magnitude of said pressure force.
- Such a reduction of the clamping action may alone be sufficient for a strapping band to be able to move between the wheel pairs of its own accord.
- the possibility of movement of the strapping band between the wheels of the wheel pair may however alternatively also be realized by virtue of an operative connection between a driven wheel and its drive being eliminated, such that both wheels of the wheel pair are rotatable freely and without a holding torque of the drive device.
- Such an elimination of an operative connection may be performed for example by way of a switchable clutch in the drive train of the driven wheel.
- switchable clutch it is also possible for the operative connection to be restored in order for a drive movement, in particular a band retraction movement, to subsequently be imparted by the driven roller to the strapping band again.
- the strapping band By way of free rotatability of the wheel pair, or at least slippage or an adequately large gap between the wheels, it is made possible for the strapping band, immediately after or even during the generation of the band loop, to discharge excess band length of the band loop through between the wheel pair, whereby it is sought to as far as possible prevent the formation of a convolution.
- An incipient excess band length in the strapping channel leads to buckling in the band loop and thus to compressive and/or bending stresses in the strapping band.
- Normal strapping bands exhibit a flexural rigidity which has the effect that such bands have the tendency to dissipate compressive and bending stresses by seeking to assume planar and rectilinearly running orientation.
- a clearance-generating device in the case of which an advancing movement of the band through the strapping device is provided for the formation of a band loop and, here, the band is clamped between a motor-driven roller and a counterpart roller, a clearance-generating device can be provided.
- the clearance-generating device may be provided for performing a clearance-generating process between the driven roller and its counterpart roller, by way of which a spacing between the driven roller and its counterpart roller is generated or enlarged and is subsequently reduced in size again.
- the expression “generating a clearance” may be understood to mean the generation of a spacing.
- Such a backward movement of a band section through the enlarged gap between the two rollers may take place automatically, in particular owing to the impetus or the kinetic energy present in the band owing to the band advancement that has previously taken place and the flexural rigidity of the band, without the need for a corresponding motor-generated drive movement to be imparted to the band in the same direction.
- the clearance-generating process between the two rollers is advantageously possible for the clearance-generating process between the two rollers to be eliminated again before the band retraction process effected by motor drive movement, and for the two rollers to be placed in contact with one another again.
- the clearance-generating process is thus performed at a time between the band advancement process and the band retraction process.
- a time overlap between the band advancement process and/or the band retraction process, on the one hand, and the clearance-generating process, on the other hand, is possible here but is not imperative.
- the non-motor-driven counterpart roller may be arranged on a rotatable eccentric.
- the clearance-generating device may act on the eccentric in order, by way of rotation of the eccentric and the eccentricity, to generate between the two rollers a gap which is greater than the band thickness.
- the eccentric can be rotated in the then opposite direction again, whereby the two rollers clamp the band between them again and a band retraction process can be performed by way of the two rollers.
- Said embodiment of the present disclosure has inter alia the advantage that a fast movement of the counterpart roller for the generation of a spacing to the driven roller, and an advancing movement toward the driven roller again, are possible by way of an eccentric with a relatively small structural space requirement.
- the spacing between the two rollers for the clearance-generating process may self-evidently also be realized in some other way, for example by way of a pivoting movement or a linear movement of at least one of the two rollers.
- the clearance-generating movement is realized by way of a linearly movable driven element such as for example a stroke-performing piston.
- a linearly movable driven element such as for example a stroke-performing piston.
- stroke-performing elements are available in a variety of forms and with different drive principles. With such stroke-performing elements, it is possible the drive movement to form particularly functionally reliable clearance-generating devices. Furthermore, with such drive elements, it is also possible with relatively little outlay for existing strapping apparatuses to be retrofitted with a clearance-generating device.
- a further embodiment of the present disclosure may provide, for the tensioning device, that, in the region of the circumferential surface of the tensioning wheel, there is provided on the tensioning wheel at least one movable spacer element which can be arranged in a first position and in a second position that differs from said first position, wherein, in the first position, the spacer element can be arranged at least in sections with a first spacing to the axis of rotation of the tensioning wheel and, in the second position, can be arranged with a second spacing, at least in sections, to the axis of rotation of the tensioning wheel, the first spacing differs here from the second spacing, and the spacer element, in at least one of the two positions, projects beyond the circumferential surface of the tensioning wheel.
- This embodiment thus makes it possible, by way of the at least one spacer element, for the strapping band to be prevented from coming into contact with the surface of the tensioning wheel when the spacer element assumes its position in which it projects at least in sections beyond the circumferential surface of the tensioning wheel.
- the spacer element can be transferred at least in sections from the position with the relatively large radial spacing to the axis of rotation into the other position with the relatively small radial spacing to the axis of rotation.
- the expression “externally applicable” may in this case be understood in particular to mean that the force is applied by an element which does not belong to the tensioning wheel or to the spacer element itself.
- the spacer element may be in the form of a passive element with regard to its change in position or the change in its geometrical shape.
- a structurally simple and nevertheless compact embodiment of the present disclosure may provide that the spacer element is arranged so as to be rotatable together with the tensioning wheel.
- the at least one spacer element assumes its first position during the band retraction phase, such that, during the band retraction phase, the strapping band is arranged against the at least one spacer element of the tensioning wheel and thus with a spacing to the circumferential surface of the tensioning wheel.
- the band is thus ideally prevented by the spacer element from coming into contact with the circumferential surface of the tensioning wheel during the band retraction phase. If such contact is not entirely avoidable, said contact should however at least be reduced to the greatest possible extent by the spacer element.
- the at least one spacer element For the tensioning phase or the tensioning process, it is by contrast possible, in certain embodiments of the present disclosure, for the at least one spacer element to be moved with at least one of its sections into the second position thereof in which, at those points of the circumferential surface at which the tensioning wheel is looped around by the strapping band, said at least one spacer element is arranged no higher than the same height as the circumferential surface, or is arranged lower than said circumferential surface. In this way, the spacer element leaves the circumferential surface free for the desired contact with the circumferential surface during the tensioning process.
- both passive and active spacer elements may be provided for the purposes of moving the at least one spacer element into its two positions.
- Active elements may be understood as elements which perform a change in position or shape automatically, for example elements which perform self-generating changes in position and/or shape of the spacer element through the use of hydraulic or pneumatic energy or the use of electrical or magnetic energy.
- certain embodiments include passive spacer elements, that is to say spacer elements which have a change in position and/or shape externally forcibly imparted to them, without the spacer element itself contributing to this.
- a change in position or shape may be realized for example by way of a counterpart roller which imparts a pressure force in the direction of the tensioning wheel and presses the band against the spacer element.
- the region of the spacer element In the presence of a correspondingly high force coordinated with the characteristics of the spacer element, it is possible in this way for the region of the spacer element to be provided with a smaller spacing to the axis of rotation of the tensioning wheel than in the unloaded state.
- the change in spacing may be utilized to the effect that, in the region of the counterpart roller, the strapping band bears now not against the spacer element but against the circumferential surface of the tensioning wheel.
- Another embodiment of the present disclosure may provide both a counterpart roller, which imparts force in the direction of the tensioning wheel, and the utilization of the band for generating the change in position.
- the change in position and/or shape of the spacer element may be realized in a particularly functionally reliable manner.
- the band is forced against the spacer element by way of a counterpart roller or some other suitable element and, in this way, the spacer element is, at least in the region of the counterpart roller, forced back such that the band comes into contact with the circumferential surface. In this way, the band enters into engagement with the tensioning wheel, whereby it is possible to commence with increasing the band tension.
- the band begins to lie against the spacer element over an at least substantially predetermined wrap angle corresponding to its provided band guidance around the tensioning wheel.
- the pressure force it is then also possible for the pressure force to be increased to a magnitude sufficient to force the spacer element back in the region of contact with the band, in such a way that the band is, over its wrap angle on the tensioning wheel, in contact with the circumferential surface of said tensioning wheel.
- the spacer element it is particularly advantageous for the spacer element to be forced back to such an extent that the spacer element, at least over a part of the wrap angle (and in certain embodiments substantially over the entire wrap angle) does not project beyond the contact region of the circumferential surface with the band. It is thus possible for the tensioning wheel to remain in engagement by way of its non-smooth circumferential surface even in the presence of further increasing band tension, and the band tension can be increased up to an intended value.
- the expression “do not project beyond the circumferential surface” can also be understood to encompass arrangements in which the spacer element projects only slightly beyond the circumferential surface, and the strapping band, for example owing to its elasticity and deformability, can come into contact with the circumferential surface despite said small projecting length.
- the circumferential surface of the tensioning wheel may, at least over a part of the length of the circumference, be equipped with a groove in which, as a constituent part of the spacer element, there may be arranged a ring element which can be arranged at least in sections in different positions.
- the ring element may advantageously be arranged in a first position, in which it is elevated at least in sections in relation to the circumferential surface, and in a second position, in which the ring element, at least in sections, does not project beyond the circumferential surface.
- the spacer element such as for example the ring element, prevents the strapping band from coming into contact with the surface, which is intentionally kept non-smooth, of the tensioning wheel.
- a particularly advantageous solution may provide that the ring element extends substantially over the entire circumference of the tensioning wheel and is arranged in a groove which extends over the circumference of the tensioning wheel.
- the ring element may be forced into the groove by the strapping band under pressure loading, such that, owing to the ring element being forced back in this way, it is the case along a wrap angle that the ring element no longer projects beyond the circumferential surface, and the strapping band can come into contact with the circumferential surface of the tensioning wheel.
- the ring element may be designed so as to be forced back into the groove in the described manner only under the action of a certain minimum force acting on the ring element. Said minimum force may be predetermined such that it is reached during the tensioning process but not during the band retraction process.
- the ring element, or other embodiments of the spacer element it is possible for the ring element, or other embodiments of the spacer element, to be of resiliently elastic form, whereby said ring element immediately and automatically restores itself when correspondingly relieved of the band pressure after having previously been subjected to load. Aside from a high level of functional reliability, this solution also makes it possible to avoid a supply of external energy.
- the tensioning wheel rotates and, in relation to a positionally static polar coordinate system of the tensioning wheel, the spacer element is forced into the groove at the at least substantially always identical circumferential section of the tensioning wheel, whereas, at the remaining circumferential section, against which the strapping band does not bear, the spacer element projects in relation to the circumferential surface.
- FIG. 1 s a highly schematized illustration of a strapping apparatus according to the present disclosure which is equipped with a strapping head according to the present disclosure.
- FIG. 2 is a perspective illustration of a strapping head according to the present disclosure.
- FIG. 3 is a perspective illustration from above of the strapping head from FIG. 2 integrated into a band guide of a strapping apparatus.
- FIG. 4 shows a side view of the strapping head from FIG. 2 , in the case of which a component is situated in a pivoted-out servicing position.
- FIG. 5 is a perspective partial illustration of the strapping head from FIG. 2 , with the band drive device being illustrated.
- FIG. 6 shows a front view of the band drive device from FIG. 5 .
- FIG. 7 is a perspective illustration of a tensioning wheel according to the present disclosure with a partial illustration of the knurling of the circumferential surface of the tensioning wheel.
- FIG. 8 shows a front view of the tensioning wheel from FIG. 7 .
- FIG. 9 is a cross-sectional illustration of the tensioning wheel along a diameter line.
- FIG. 10 shows a component of a lever mechanism for a counterpart roller of the band drive device.
- FIG. 11 shows a further component of the lever mechanism of the counterpart roller in a perspective illustration.
- FIG. 12 shows the component from FIG. 11 in a front view.
- FIG. 13 is a sectional illustration of the component from FIGS. 11 and 12 .
- FIG. 14 is an exploded illustration of a further exemplary embodiment of a tensioning wheel.
- FIG. 15 is a perspective illustration of the tensioning wheel from FIG. 14 .
- FIG. 16 shows a front view of the tensioning wheel from FIGS. 14 and 15 .
- FIG. 17 is a sectional illustration of the tensioning wheel from FIGS. 14-16 .
- FIG. 18 shows a further exemplary embodiment of a band drive device according to the present disclosure with a clearance-generating device in a partial illustration of a strapping head.
- FIG. 19 shows the band drive device from FIG. 18 in an illustration in which a clearance has been generated between a counterpart roller and the driven roller that interacts therewith.
- FIG. 1 shows a strapping apparatus 1 which is equipped with a controller 2 , a supply device 3 for storing and making available a strapping band, and with a strapping head 5 .
- the strapping head 5 serves inter alia for the generation of an advancement movement and for the generation of a retraction movement of the strapping band.
- Said strapping head is furthermore equipped with a tensioning device, for imparting a band tension to a band loop, and a fastening device for generating a fastening on the strapping band.
- the strapping apparatus has a band guide 6 by way of which the band can be mechanically and automatically laid around a packaged item 7 on a predefined path.
- a welding and clamping unit 16 is also integrated into the strapping head 5 . Aside from the strapping head 5 , these are components that are known per se of strapping apparatuses.
- the strapping head 5 which is arranged together with the band guide 6 on a frame 8 and which is separately illustrated in FIG. 2 has a band drive device 15 .
- Band drive devices are basically already known, for which reason substantially the differences in relation to previously known band drive devices will be discussed below.
- the band drive device according to this exemplary embodiment may be equipped in particular with one or more roller pairs 11 , 12 ; 13 and possibly with further individual diverting rollers. The latter however do not participate in the generation of the band movement and are provided only for determining the band running direction. Of the three rollers 11 , 12 , 13 in the exemplary embodiment which generate the band movements, at least one of the rollers 11 , 12 , 13 should be motor-driven for the purposes of generating a band advancement or band retraction movement.
- the strapping head 5 has two components: a control component 16 and a band handling component 17 .
- the control component 16 aside from the execution of control functions for the components of the strapping device, has further functions, for example the generation of fastenings between the two belt layers of a strap and the cutting of the strapping band from the band supply.
- the control component 16 is in this case mounted on a partial carrier 18 of the strapping head, wherein the partial carrier 18 is in turn detachably fastened to a common main carrier 19 of the strapping head 5 .
- the partial carrier 18 of the control component 16 is pivotable about an axis 23 .
- the elements of the band handling component 17 are fastened, without a dedicated partial carrier, directly to the main carrier 19 of the strapping head.
- the control component 16 is provided substantially for performing control and coordination functions out of the functions performed by the strapping head.
- the band handling component 17 and the components attached thereto are, by contrast, provided for acting directly on the strapping band.
- a band advancement device 20 , a band retraction device 21 and a tensioning device 22 are integrated into the band handling component 17 of the strapping head 5 .
- common rollers 11 , 12 ; 13 are provided for the band advancement, band retraction and tensioning devices 20 , 21 , 22 .
- two rollers 11 , 12 are motor-driven rollers.
- the two rollers 11 , 12 are driven by the same (only one) motor 14 , in the exemplary embodiment an electric motor.
- the roller 11 is provided both as a drive wheel for the band advancement (band advancement wheel) and as a drive wheel for the band retraction (band retraction wheel).
- the roller 11 can be driven in both directions of rotation by the same drive motor 14 .
- the direction of rotation counterclockwise is the band advancement direction
- the direction of rotation clockwise is the band retraction direction.
- the motor drive movement is transmitted to both wheels or rollers 11 , 12 by the common motor 14 by way of a mechanism device.
- the mechanism device 14 a comprises a toothed-belt mechanism which transmits the drive movement from the motor shaft to a further shaft running parallel to the motor shaft.
- On said further shaft there are arranged two gearwheels which belong in each case to a further one of two partial mechanisms of the mechanism device.
- One of said two partial mechanisms of the mechanism device transmits the motor drive movement to the roller or the wheel 11
- the other partial mechanism transmits the motor drive movement to the tensioning wheel 12 .
- both the tensioning wheel 12 and the wheel 11 rotate in different directions of rotation.
- the roller 11 is arranged above the roller 12 .
- the roller 12 is a constituent part of the tensioning device 22 and has the function of the tensioning wheel. Said roller has a considerably greater diameter than the roller 11 .
- the tensioning wheel 12 owing to the rigid connection to the motor 14 and the drive movements in both directions of rotation performed by the motor, can likewise be driven in both directions of rotation.
- the tensioning wheel however utilizes only the drive movement in the tensioning direction, that is to say the clockwise direction of rotation as viewed in the illustration of FIG. 6 .
- a release of tension from the band section which is situated in the strapping head, and which is no longer part of the band loop may be realized by way of a rotational movement of the tensioning wheel, taking place after the tensioning process, in the direction of rotation opposite to that during the tensioning process.
- the drive movements both for the tensioning movement and for the tension-relieving movement originate from the same drive motor as for the roller 11 .
- a switchable clutch to be provided in the drivetrain (not illustrated in any more detail) from the motor to the two rollers 11 , 12 , by way of which clutch the drive movement can be conducted either to the roller 11 or to the roller 12 .
- the tensioning wheel is in turn capable of being driven in both directions of rotation, it may also be provided that the tensioning wheel can also be driven only in the direction of rotation provided for the tensioning process.
- the roller 13 is adjacent both to the roller 11 and to the tensioning wheel 12 .
- the roller 13 is not driven in rotation and is pivotably articulated by way of a pivoting device.
- the pivoting device is operatively connected to a drive by way of which the roller can perform (motor-) driven pivoting movements.
- the roller 13 which functions as counterpart roller can be placed either in contact with the roller 11 or in contact with the tensioning wheel 12 , wherein, in the respective end position of the pivotable roller 13 , the strapping band is situated in each case between one of the rollers 11 , 12 and the roller 13 .
- the counterpart roller 13 forces the band against the corresponding roller 11 , 12 such that the corresponding roller 11 , 12 can transmit its rotational movement with the least possible slippage as an advancement, retraction or tensioning movement, and possibly as a tension-relieving movement, to the strapping band.
- the counterpart roller 13 is thus, together with the roller 11 , both a constituent part of the band advancement device and a constituent part of the band retraction device. Together with the tensioning wheel 12 , the counterpart roller 13 is also a constituent part of the tensioning device 22 .
- the fourth roller that has hitherto been conventional in previously known solutions to be dispensed with.
- the drive roller and the tensioning wheel are in each case fixedly assigned one of two counterpart rollers.
- the 3-roller solution according to the present disclosure can permit a considerably more compact embodiment in relation thereto.
- the rollers 11 , 12 , 13 are, in the strapping head 5 , furthermore a constituent part of a band guide channel 28 which predefines the profile and the advancement and retraction path of the band.
- the band guide channel 28 is in turn part of the band guide 6 .
- the strapping head 5 has a first interface 29 at which the strapping head 5 adjoins the supply roll side of the band guide. That end of the band guide channel 28 which is formed here is in the form of a quick-change interface.
- This has a channel piece 31 which can be clamped to the strapping head by way of a pivotable clamping lever 30 and through which the band is supplied into the strapping head.
- the channel piece 31 ends directly in front of the circumferential surface 11 a of the roller 11 , such that the strapping band can be supplied at least approximately tangentially to the circumferential surface 11 a of the roller 11 . If the roller 13 is situated in its end position in which it is pivoted toward the roller 11 , the band is led through between the rollers 11 , 13 , wherein the roller 13 forces the band against the roller 11 .
- the band passes, in its further progression, to the tensioning wheel 12 .
- a circular-arc-shaped channel section 28 a which extends over approximately 180° of the circumference of the tensioning wheel 12 is formed by way of suitable channel-forming means.
- the channel section 28 a is formed so as to be considerably wider than the band thickness.
- the inner delimitation of the channel section is formed by that section of the circumferential surface 12 a of the tensioning wheel 12 which is situated in each case in the region of the channel section.
- the outer delimitation of the channel section 28 a as viewed radially has guide plates and an outer channel segment which is pivotable together with the counterpart roller 13 , by way of which outer channel segment the outer channel section can be kept closed despite the pivotable counterpart roller 13 being situated in the region of the outer channel section.
- the pivotable channel segment 33 or some other element of similar action there would possibly be an open point of the channel section at least in one of the two pivoting end positions of the counterpart roller 13 , which open point could possibly have an adverse effect with regard to reliable band guidance.
- FIGS. 7, 8 and 9 show the tensioning wheel in three illustrations.
- Said tensioning wheel has a ring 37 which is equipped with a recess 38 which is provided for the connection of the tensioning wheel 12 to a shaft of the drive, in particular to a shaft of a mechanism of the drive.
- FIG. 2 shows the tensioning wheel 12 mounted on the shaft.
- the circular tensioning wheel has a circumferential surface 12 a with an at least substantially constant width.
- the tensioning wheel 12 is equipped, on its circumferential surface 12 a , with a knurling or toothing 39 by way of which the engagement conditions of the tensioning wheel 12 on the strapping band are improved.
- any other geometrically defined or undefined roughening of the circumferential surface 12 a of the tensioning wheel it would also be possible for any other geometrically defined or undefined roughening of the circumferential surface 12 a of the tensioning wheel to be provided, by way of which possible slippage between the tensioning wheel and the strapping band during the tensioning process can be at least substantially prevented.
- a groove 40 with a relatively small width is formed over the entire circumference of the circumferential surface 12 a at least approximately centrally—in relation to the width of the tensioning wheel 12 —and so as to be spaced apart from the lateral edges of the tensioning wheel, which groove is formed so as to be considerably deeper than it is wide.
- two resiliently elastic O-rings 43 , 44 are situated one above the other in the groove 40 , said O-rings being arranged radially one behind the other in the groove 40 .
- one of the O-rings 43 is arranged with a relatively small spacing to the axis of rotation of the tensioning wheel 12
- the other O-ring 44 is arranged with a relatively large spacing to the axis of rotation of the tensioning wheel 12 .
- the width of the O-rings 43 , 44 is in this case provided so as to approximately correspond to the width of the groove 40 .
- the two O-rings 43 , 44 are situated entirely within the groove 40 .
- the two O-rings 43 , 44 are formed from resiliently elastic material.
- a ring 45 which is provided as a spacer element and which, in the exemplary embodiment, is formed from a metallic material.
- the ring 45 is elastically deformable. It would likewise be possible for the ring to be of substantially rigid or dimensionally stable form. To realize said elastic characteristics of the ring, it would also be possible for the ring 45 to be formed from one or more materials other than a metallic material, for example from an elastic plastic.
- said metal ring 45 is, in terms of its cross section, provided so as to have a width B smaller than its height H.
- the height of the O-ring is, with regard to the groove depth and the height of the O-rings, configured such that the ring projects with a height H 1 out of the groove 40 .
- the ring 45 projects beyond the circumferential surface 12 a of the tensioning ring 12 , in particular over its entire circumference or over the entire circumference of the tensioning ring 12 .
- the strapping band is pushed at high speed, with its free band end first, from the strapping head 5 through the band guide 6 .
- the counterpart roller 13 is in contact with one side of the band.
- the band is forced with its other side against the motor-driven roller 11 by the counterpart roller.
- the rotational drive movement of the roller 11 in the advancement direction is in this way transmitted to the strapping band, which effects the advancement movement thereof in the advancement direction.
- the band comes into contact with the tensioning wheel 12 , but without exerting a significant pressure on the tensioning wheel 12 .
- the band end After the band has been pushed all the way through the band guide 6 , the band end reaches the closure head again. Here, the band end actuates a limit switch, whereby the advancement movement is stopped and the band end is clamped.
- the control component 16 which, for this purpose, is equipped with a motor-driven camshaft control arrangement such as is basically known.
- the camshaft control arrangement of the control component 16 now sets the roller 11 in motion in a direction of rotation reversed in relation to the advancement direction.
- the strapping band which remains clamped between the roller 11 and the counterpart roller 13 , is hereby moved in the reverse direction, that is to say in the band retraction direction 48 .
- the circumferential length of the band loop, the band end of which remains clamped, is hereby continuously shortened.
- the band is hereby pulled out of the band guide 6 and, as a result, laid around the respective packaged item.
- FIG. 6 illustrates the tensioning wheel 12 during the band retraction process.
- the strapping band bears against the tensioning wheel 12 substantially over the entire circular-arc-shaped channel section 28 a , similarly to the situation also encountered during the subsequent tensioning process.
- the band is duly retracted here, but, owing to its ability to yield to said movement by moving, as intended, out of the band guide, it is nevertheless the case during said phase that only a relatively low band tension is applied to the band of the band loop.
- the controller switches from band retraction to generation of a band tension, whereby it is the intention for the band laid against the packaged article to be pulled taut.
- the counterpart roller 13 is pivoted from its position of contact against the roller 11 into a position of contact against the tensioning wheel 12 .
- the tensioning wheel 12 which is rotated in the same direction of rotation as the roller 11 was previously, rotates at a lower rotational speed but with a greater torque, and pulls further on the strapping band.
- the band no longer bears against the roller 11 , which continues to be driven in the exemplary embodiment and which rotates at a higher speed, in such a way that the roller 11 could transmit its movement to the band. Since, at this stage, the strapping band already bears against the packaged article, the band is, by the tensioning wheel 12 , retracted at most over a short length in relation to the band retraction phase. During said tensioning phase, it is in particular the case that a relatively high band tension is applied to the band.
- the pressure of the counterpart roller 13 in the direction of the tensioning wheel and the band situated in between causes the ring 45 to be forced in the direction of the groove base and thus also in the direction of the axis of rotation of the tensioning wheel 12 as viewed in a substantially radial direction.
- the band bears against the ring 45 and forces the latter likewise, at least in the region of the counterpart roller 13 , in the direction of the groove base.
- the ring 45 has, in the region of the counterpart roller 13 , a smaller spacing to the axis of rotation of the tensioning wheel than in its unloaded state, for example during the band advancement or the band retraction phase.
- the ring 45 is deformed possibly elastically as a result, and, along that circumferential section in which the strapping band does not bear against the tensioning wheel, said ring can partially (with regard to its height) emerge from the groove again.
- the ring 45 may in this case project out of the circumferential surface to a greater extent than in the unloaded state, in the case of which it projects with a height H 1 .
- the counterpart roller 13 can advantageously be forced with different pressing forces firstly against the roller 11 (advancement roller or retraction roller) and secondly against the tensioning wheel 12 (during the use of the strapping device in each case with a strapping band situated in between).
- Higher pressing forces against the tensioning wheel than the possible pressing forces against the roller 11 can be advantageous for high functional reliability and for the possibility of applying high band tensions to the strapping band. Therefore, below, it will be discussed how, in one embodiment of the present disclosure, despite the pivoting movement of the counterpart roller 13 between two end positions, different pressing forces can be realized in the end position.
- the counterpart roller 13 is arranged on an eccentric 50 which, in turn, is arranged on a shaft 51 of a carrier 52 .
- the carrier has, spaced apart from the shaft 52 , a receptacle 53 which is provided for arrangement on the bearing point 54 of the roller 11 ( FIGS. 5 and 6 ).
- the receptacle 53 is freely rotatable about its axis of rotation on the bearing point 54 of the roller 11 and can thus perform pivoting movements about its axis of rotation.
- a parallelogram which has multiple levers 57 , 58 , 59 which are pivotably articulated on one another.
- the parallelogram 56 has a long vertical lever 57 , a horizontal lever 58 and a short vertical lever 59 .
- the parallelogram is pivotably articulated on the long vertical lever 57 and on the short vertical lever 59 .
- the levers 57 and 59 have pivot bearing points 60 , 61 for this purpose. Via a bell-shaped curve 62 , it is possible for a rotational movement to be transmitted to the long vertical lever 57 , which rotational movement leads to the pivoting movement of the lever 57 about its pivot bearing point 60 .
- the pivoting movement of the lever 57 takes place clockwise.
- the lever 58 also pulls said short vertical lever in the direction of the lever 57 , whereby the vertical lever 59 is, in the illustration of FIGS. 11 and 12 , likewise pivoted clockwise about its pivot bearing point 62 .
- an oblique surface 64 formed on the short vertical lever 59 pushes against a bearing 51 arranged on the shaft 51 .
- the oblique surface performs a movement clockwise (in the illustration of FIG. 12 ) and has the tendency to assume a horizontal orientation.
- the carrier 52 performs a pivoting movement, whereby the counterpart roller 13 is pivoted from its end position against the roller 11 in the direction of the tensioning wheel 12 .
- the counterpart roller When it reaches the tensioning wheel, the counterpart roller bears against the tensioning wheel and can perform no further pivoting movement.
- the lever 57 pivots further, whereby the bearing point 65 of the eccentric 50 is moved counterclockwise in the direction of an L-shaped carrier 66 .
- the bearing point 65 After the bearing point 65 pushes against the L-shaped carrier 65 , the movement of the bearing point 65 stops, and said bearing point is situated at least approximately in a line with an upper bearing point 66 , the axis of rotation 67 of the counterpart roller 13 and the axis of rotation 68 of the tensioning wheel 12 .
- a spring element that has hitherto generated the pressing force of the counterpart roller 13 is, as a result, no longer active.
- a spring element 70 arranged between the two parts 58 a , 58 b of the lever is hereby compressed, whereby the spring force thereof increases. This leads to a torque of the lever 59 about the pivot bearing point 61 with the lever arm of the spacing of the pivot bearing point 61 from the articulation point 71 of the lever 58 on the lever 59 .
- a restoration of the parallelogram can be realized by way of a further spring 73 arranged on the peg 72 of the lever 5 .
- FIGS. 1 to 13 Alternative embodiments of components and assemblies discussed above will be described below. Here, substantially only differences in relation to the corresponding components from FIGS. 1 to 13 will be discussed. Where said embodiments include identical or similar configurations to those in the exemplary embodiment of FIGS. 1 to 13 , these will not be discussed in any more detail below; the content of disclosure of the exemplary embodiments of FIGS. 1 to 13 is however also incorporated by reference for the exemplary embodiments of FIGS. 14 to 19 .
- FIGS. 14, 15, 16 and 17 illustrate a further embodiment of a tensioning wheel 112 according to the present disclosure.
- the tensioning wheel 112 may be divided longitudinally in terms of its width, approximately in the center, wherein the two parts 112 b , 112 c of the tensioning wheel 112 are detachably connectable to one another by way of suitable fastening elements, for example screws 114 .
- suitable fastening elements for example screws 114 .
- an encircling groove 140 is formed in the outer ring 137 of the tensioning wheel 112 , which groove is open toward the circumferential surface 112 a of the tensioning wheel 112 and is narrowed or decreased in size toward said circumferential surface.
- One or more restoring elements may be arranged in the groove 140 .
- a restoring element there are arranged elastic ring sections 143 , for example multiple resiliently elastic O-ring sections 143 .
- Said ring sections are distributed in the groove 140 at regular intervals with respect to one another, as is the case in the exemplary embodiment with a total of four ring sections 143 .
- the restoring elements 143 are situated below one or more spacer elements.
- only one spacer element 145 in the form of a closed ring, is provided.
- An outer diameter of the ring 145 arranged in the groove is in this case dimensioned such that, in the unloaded state of the ring 145 , said ring projects with its outer circumferential surface beyond the circumferential surface 112 a of the tensioning ring 112 .
- the ring 145 is situated with its inner circumferential surface in the groove.
- the restoring elements are attached to the inner circumferential surface of the circular and substantially dimensionally stable ring 145 . In other embodiments, it is also possible for a different number of spacer elements, and a different number of restoring elements, to be provided.
- the ring 145 which substantially cannot be deformed by the expected forces acting thereon in the exemplary embodiment, and which is thus dimensionally stable, is thus arranged slightly eccentrically in relation to the axis of rotation of the tensioning wheel during said process.
- the ring 145 hereby projects, with its section not encompassed by the wrap angle of the band, out of the groove 140 further than when the tensioning wheel is in the state in which it is not subject to load by the strapping band.
- FIGS. 18 and 19 illustrate a further exemplary embodiment of a band drive device 115 .
- Said band drive device also has only three rollers 111 , 112 , 113 which are responsible for imparting the band advancement, band retraction and band tensioning movements to the band by way of contact with the band, wherein the two rollers 111 and 112 can be driven by way of a motor, in particular by way of only one common motor.
- the relative arrangement of the axes of rotation of the three rollers 111 , 112 , 113 with respect to one another corresponds at least approximately to the arrangement of said axes of rotation in the exemplary embodiment of FIGS. 5 and 6 .
- the counterpart roller 113 is again designed to be pivotable, such that, in one pivoting position, it is provided for pressing the strapping band against the roller 111 , and in another pivoting position, it is provided for pressing the strapping band against the tensioning roller 112 .
- the pivoting mechanism, provided for this purpose, of the counterpart roller 113 , and the drive of said pivoting mechanism may in principle be of the same design as in the exemplary embodiment of FIGS. 1 to 13 . As in the exemplary embodiment of FIGS.
- the counterpart roller 113 is rotatably mounted on an eccentric 150 , such that the counterpart roller 113 performs a non-circular-arc-shaped movement during a pivoting movement from one of the rollers 111 , 112 to the respective other roller 111 , 112 .
- a clearance-generating device 180 is mounted on the eccentric 150 of the counterpart roller 113 , wherein the clearance-generating device 180 is supported with a carrier 181 on the frame of the strapping apparatus 101 .
- the bearing point 182 of the clearance-generating device on the eccentric 150 is itself arranged pivotably on the eccentric, and is in the form of a C-shaped or fork-shaped element 183 to thereby form a receptacle for one end of a piston 184 .
- Said piston 184 is arranged in displaceable fashion in the carrier 181 of the clearance-generating device 180 .
- the support point is situated immediately above the roller 111 .
- the carrier 181 of the clearance-generating device is in this case likewise mounted in pivotable fashion.
- the clearance-generating device 180 is equipped with a clearance-generating element which is provided for performing a controlled movement by way of which the counterpart roller 113 is acted on in order for the counterpart roller 113 , in its pivoted edition against the roller 111 , to be moved such that a clearance is generated, or to be lifted slightly.
- the counterpart roller 113 in its pivoted position at the roller 111 , should, even after the generation of a clearance, be able to be placed against the roller 111 again, for example likewise by way of the clearance-generating device.
- the clearance-generating element is in the form of a solenoid 186 which is arranged and mounted on the clearance-generating device 180 .
- the solenoid 186 can, by way of its piston 184 , perform a linear stroke movement along the longitudinal axis 184 a of its piston 184 .
- one end of the piston 184 is arranged in the recess, which is open toward the carrier 181 , of the C-shaped or fork-shaped element 183 .
- the end of the piston 184 and the recess of the C-shaped element may in this case be designed such that, during the clearance-generating movement, the end of the piston 184 in the C-shaped element can move relative thereto.
- the extended longitudinal axis 184 a of the piston 184 runs at least approximately through the articulation point of the C-shaped element 183 .
- a stroke movement of the piston 184 in the direction of the counterpart roller 113 thus leads to a rotational movement of the eccentric about its axis of rotation.
- the rotational movement takes place counterclockwise, as can be seen from a comparison of the two FIGS. 18 and 19 .
- the rotational movement of the eccentric 150 in turn has the effect that the axis of rotation of the counterpart roller 113 is displaced in parallel and a gap, or an enlarged gap, is formed between the roller 111 and the counterpart roller 113 .
- the width of the gap should in this case have a size greater than the thickness of the strapping band being processed in each case.
- a solenoid use may for example be made of the product GKb-32.06 from the company Isliker Magnete AG, CH-8450 Andelfingen.
- a mechanical spring element in particular at least one compression spring 188 .
- Said compression spring 188 is compressed, and thus braced in resiliently elastic fashion, during the movement of the counterpart roller 113 from the tensioning roller 112 into contact with the roller 111 .
- the electrically actuable magnetic stroke-performing piston is deactivated, and thus has no action, in this phase.
- the compression spring 188 is at least partially relaxed and the spring force acts so as to assist the force imparted by the solenoid, by way of which force the piston 184 is moved so as to generate a clearance between the counterpart roller 113 and the roller 111 .
- the solenoid or some other restoring element alone provides a force high enough for the clearance-generating process.
- the band is moved through the band guide channel 28 in a feed direction.
- the strapping band reaches the region of the end of the band guide channel, as is illustrated by way of example in highly schematized form in FIG. 1 , the band strikes a stop, or the fact that the end of the band guide channel has been reached may be detected in some other way, for example by way of a light barrier.
- a signal is generated, by way of which the control of the strapping apparatus stops the motor drive movement of the roller 111 and—at least substantially at the same time—triggers the stroke movement of the piston 184 of the solenoid.
- the stoppage of the drive movement of the roller 111 and the start of the clearance-generating process it is also conceivable for the stoppage of the drive movement of the roller 111 and the start of the clearance-generating process to have a time offset with respect to one another, that is to say for the stoppage of the drive movement to be performed before or after the start of the clearance-generating process.
- the piston 184 deploys in the direction of the C-shaped element 183 and, here, acts by way of its end on the C-shaped or fork-shaped element. Owing to its arrangement on the eccentric 150 , the eccentric is rotated during the stroke movement of the piston. In the exemplary embodiment and in the illustration of FIG. 18 , the rotational movement of the eccentric takes place through a rotational angle of less than 90° counterclockwise. The rotational movement takes place counter to the spring force of the pressure-exerting spring 190 , which in this case is compressed and is likewise articulated on the eccentric 150 .
- the strapping band which is shot at high speed through the band channel of the band guide 6 , has the tendency, owing to the sudden and abrupt stoppage of the band, to form convolutions between the rollers 111 , 112 , 113 and the end of the strapping channel.
- convolutions can lead to malfunctions.
- the band in which a clearance of the counterpart roller 113 is generated, can, in particular immediately after the stoppage of the advancement, move freely counter to the advancement direction in the direction of the band supply to the extent required for that part of the band which is possibly excess in relation to the length of the band channel, and which causes the formation of convolutions, to move back in the band guide channel.
- the controller of the strapping apparatus can then subsequently deactivate the solenoid again.
- the solenoid is rendered inactive, whereby the pressure-exerting spring 190 can move the eccentric 150 back again counter to the previous direction of rotation, and thus move the counterpart roller 113 into its position of contact with the band again, in which the band is clamped between the roller 111 and the counterpart roller 113 .
- the subsequent band retraction and tensioning process can be performed in the same way as in the embodiments of the present disclosure as per FIGS. 1 to 13 .
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Abstract
Description
- This application is a national stage entry of PCT/CH2015/000015, filed on Feb. 10, 2015, which claims priority to and the benefit of Switzerland Patent Application Nos.: (1) 183/14, filed on Feb. 10, 2014; (2) 182/14, filed on Feb. 10, 2014; and (3) 181/14, filed on Feb. 10, 2014, the entire contents of each of which are incorporated herein by reference.
- The present disclosure relates to a strapping device of a strapping apparatus for the strapping of packaged articles with a strapping band, in particular with a plastics strapping band, which is equipped with an advancement and tensioning device which are equipped with multiple wheels for transmitting an advancement, retraction and tensioning movement to the strapping band, wherein at least one of said wheels is operatively connected or operatively connectable to a drive device to set the at least one of the wheels in rotational motion about an axis of rotation for the advancement, retraction and tensioning movement.
- Strapping apparatuses of said type, like those to which the present disclosure also relates, may be formed as a static installation which is utilized for equipping relatively large packaged articles, or multiple individual packaged articles placed together to form a packaged article unit, with one or more band straps. The band straps are normally formed from a band which is drawn from a supply roll and laid as a ring-shaped strap around the packaged article. For this purpose, the strapping band is shot with its free end first into a channel of the strapping apparatus, which channel surrounds the packaged article, with a spacing, in the manner of a portal or in ring-shaped fashion. Normally, as soon as the band end has reached a particular point in the channel, the band end is clamped and the band is then retracted again. As a result, the loop of the strapping band is tightened and the band passes out of the channel and into contact with the packaged article. Subsequently, the band is pulled taut and, in the process, a band tension is applied to the band, and the band ring or the band loop is equipped with a fastening and is cut off from the supply roll. As strapping band, use is made both of metallic bands and of plastics bands. The strapping apparatuses are normally adapted to the strapping band types used therewith, in particular with regard to the connecting device by way of which two band layers, which lie one over the other in sections, of the strapping bands can be non-detachably connected to one another.
- In the case of previously known solutions, the strapping apparatus generally has a band advancement device for the advancement of the strapping band during the formation of a band loop, a band retraction device for the retraction of the strapping band after the formation of the band loop, for the purposes of causing the strapping band to be laid against the packaged article, and a tensioning device, by way of which a band tension in the strapping band laid against the packaged article can be increased, that is to say the band is laid taut against the packaged article. These three functional components normally require a multiplicity of components and in particular rollers to impart the individual movements to the band in a functionally reliable manner. As a result of this, the strapping device, which is normally in the form of a strapping head, is of relatively large construction, and requires a large volume in the strapping apparatus. Furthermore, this results in a high weight of the strapping device.
- The present disclosure is therefore based on the object of improving a strapping apparatus for strapping packaged articles with a strapping band such that the strapping head can be designed to be as compact as possible.
- Said object is achieved by way of a strapping device of the type mentioned in the introduction, in the case of which, for the contact with the strapping band during the execution and imparting of the advancement, retraction and tensioning movement to the band, a total of at most three rollers are provided on the strapping head, which rollers come into contact with the strapping band in conjunction with said functions, and here, the at most three rollers can, in each case pairwise in different combinations with one another, be placed in contact with the strapping band on both sides of the strapping band. In an alternative wording, the present disclosure can thus also be seen in that, in the case of a strapping device in which it is the case that, for the band handling, that is to say for the action on the strapping band during the generation of the band movements, a band advancement device, a band retraction device and a tensioning device of the strapping device are provided, and here, a roller whose circumferential surface is provided for making contact with the strapping band is a constituent part of the tensioning device and of the band advancement device and of the band retraction device. With the present disclosure, it is thus proposed that a roller of the strapping device, which roller is provided in conjunction with the band movement and for making contact with the strapping band, performs multiple functions and is thus assigned to multiple functional units of the strapping device. In this way, it is possible to realize a reduction in the hitherto normally provided number of rollers or wheels. The previously customary four rollers for the band handling in conjunction with the imparting of the movement and tension to the band can, by way of the present disclosure, be reduced to only three rollers. Strapping devices according to the present disclosure, which are normally in the form of so-called strapping heads, can be made more compact through the omission of at least one previously provided roller. Furthermore, through the omission of one or multiple rollers, it is possible for the band profile through the strapping head to be simplified, which can furthermore contribute to an increase in functional reliability of such strapping heads.
- In certain refinements, by way of the at most three rollers according to the present disclosure, it is also possible, after the tensioning process, for that band section which is situated in the strapping device to be at least partially relieved of tension. Through the reduction of the band tension in the region of the strapping device, the band can be processed more easily during the generation of the connection between the two band layers and during the cutting of the band from the band supply, which has an advantageous effect on the working result. The tension-relieving process may be realized by way of a motor-driven rotational movement of the tensioning wheel in a direction of rotation of the tensioning wheel which corresponds to the opposite of the direction of rotation provided previously during the tensioning process. Since the band loop that has already been generated can be held in position here by way of suitable clamping means, the tension-relieving process has no influence on the band tension in the band loop.
- The said one roller may advantageously be a counterpart roller which is itself not driven in rotation about its axis of rotation and which is thus freely rotatable about its axis of rotation. A position of the said one roller should however advantageously be variable in relation to at least one of the two other rollers by way of a driven movement. For the change in position, the said one roller may be attached to a movement device which is driven by motor means or other means, by way of which movement device the movement for the change in position is effected. At least one of the three rollers, and in certain embodiments only one of the three rollers, should be movable alternately in the direction of in each case one of the two other rollers in order, in a movement end position, to bear together with the in each case one other roller against the band. In such embodiments of the present disclosure, the movable only one roller may thus, as a counterpart roller for two driven rollers, serve primarily for alternately forcing the band against one driven roller and against the other driven roller to reduce or prevent slippage between the band and the driven rollers.
- In a further embodiment according to the present disclosure, the movable roller may be provided for performing pivoting movements, in particular driven pivoting movements. Pivoting movements can be generated with particularly little outlay for the purpose of generating the changes in position provided according to the present disclosure. Corresponding movement devices and the drive thereof may be realized in a compact construction and integrated, with little space requirement, in a strapping device according to the present disclosure.
- In one embodiment of the present disclosure, the movement of the movable roller may be in the form of a combined stroke movement and pivoting movement. By contrast to a pure pivoting movement along a radius, it is possible in this way to realize either a pivoting movement about a radius with a superposed stroke movement, or else a stroke movement and pivoting movement performed successively in terms of time, by way of which movement it is possible to realize particularly advantageously optimum movement paths and positions of contact of the movable roller against the two further rollers.
- An embodiment of the present disclosure has proven to be particularly advantageous in which a first roller is formed as a tensioning roller of the tensioning device and a second roller is formed as a roller of the band advancement and band retraction device, the first and the second roller are operatively connected or operatively connectable to one or more drives for the purposes of generating driven rotational movements of the first and of the second roller, and the third roller, which is movable in terms of its position, is arranged so as to be movable in driven fashion between positions of contact with the first and with the second roller. The movable roller is thus advantageously movable between two end positions and can be arranged in said two end positions, in which the movable roller is provided for performing either a function of the tensioning device or a function of the band advancement and/or band retraction device.
- A further embodiment of the present disclosure—which may also be of independent significance independently of the number of wheels, rollers and motors used for the imparting of movements to the band and independently of the design of the tensioning wheel—may provide an actuable means by which at least one wheel of a wheel pair of the advancing device can be switched into a state in which the strapping band can be displaced between the wheel pair in a direction opposite to the band advancement movement, without a corresponding motor drive movement being transmitted to the strapping band. With the present disclosure, provision is thus made for the state of the wheel pair to be changed from a state in which the band is clamped between said wheels, which state permits in particular the advancement of the band, into a state in which the band can move through between the wheel pair regardless of a driven movement of a wheel of the wheel pair. According to the present disclosure, the clamping state between the wheel pair, which clamping state is provided for the transmission of a motor drive movement via one of the two wheels to the strapping band, is reduced at least to such an extent that slippage or an increased gap can form between the band and the wheel pair. If an enlarged gap between the circumferential surfaces of the wheels is generated in the event of the clamping action being eliminated, said gap should be larger than the band thickness. The clamping action may for example be reduced simply by virtue of a pressure force with which the two wheels are pressed against one another being reduced, for example by way of a variably adjustable magnitude of said pressure force. Such a reduction of the clamping action may alone be sufficient for a strapping band to be able to move between the wheel pairs of its own accord.
- The possibility of movement of the strapping band between the wheels of the wheel pair may however alternatively also be realized by virtue of an operative connection between a driven wheel and its drive being eliminated, such that both wheels of the wheel pair are rotatable freely and without a holding torque of the drive device. Such an elimination of an operative connection may be performed for example by way of a switchable clutch in the drive train of the driven wheel. By way of said switchable clutch, it is also possible for the operative connection to be restored in order for a drive movement, in particular a band retraction movement, to subsequently be imparted by the driven roller to the strapping band again.
- By way of free rotatability of the wheel pair, or at least slippage or an adequately large gap between the wheels, it is made possible for the strapping band, immediately after or even during the generation of the band loop, to discharge excess band length of the band loop through between the wheel pair, whereby it is sought to as far as possible prevent the formation of a convolution. An incipient excess band length in the strapping channel leads to buckling in the band loop and thus to compressive and/or bending stresses in the strapping band. Normal strapping bands exhibit a flexural rigidity which has the effect that such bands have the tendency to dissipate compressive and bending stresses by seeking to assume planar and rectilinearly running orientation. This is advantageously utilized by the present disclosure in that, through the creation of a possibility for movement of the band through between the wheel pair, excess band length can move in particular of its own accord out of the band channel again between the wheels owing to the self-relaxation of the band.
- In a refinement of said further aspect of the present disclosure, a strapping device in the case of which an advancing movement of the band through the strapping device is provided for the formation of a band loop and, here, the band is clamped between a motor-driven roller and a counterpart roller, a clearance-generating device can be provided. According to this aspect of the present disclosure, in the case of a strapping device, the clearance-generating device may be provided for performing a clearance-generating process between the driven roller and its counterpart roller, by way of which a spacing between the driven roller and its counterpart roller is generated or enlarged and is subsequently reduced in size again. In this context, therefore, the expression “generating a clearance” may be understood to mean the generation of a spacing.
- With this measure according to said further aspect of the present disclosure, it is possible in a particularly functionally reliable manner for the formation of a convolution in the band noose or loop, in particular in the region of a band drive device of the strapping device, such as has hitherto often arisen after the completion of the band advancement process in the case of a high band advancement speed and can lead to malfunctions of the strapping device, to be at least substantially avoided. Excess band can move in the direction of the band store again of its own accord through the gap, enlarged owing to the clearance-generating process, between the two rollers. Such a backward movement of a band section through the enlarged gap between the two rollers may take place automatically, in particular owing to the impetus or the kinetic energy present in the band owing to the band advancement that has previously taken place and the flexural rigidity of the band, without the need for a corresponding motor-generated drive movement to be imparted to the band in the same direction.
- It is advantageously possible for the clearance-generating process between the two rollers to be eliminated again before the band retraction process effected by motor drive movement, and for the two rollers to be placed in contact with one another again. The clearance-generating process is thus performed at a time between the band advancement process and the band retraction process. A time overlap between the band advancement process and/or the band retraction process, on the one hand, and the clearance-generating process, on the other hand, is possible here but is not imperative.
- In a further expedient embodiment of the present disclosure according to this aspect, the non-motor-driven counterpart roller may be arranged on a rotatable eccentric. Here, the clearance-generating device may act on the eccentric in order, by way of rotation of the eccentric and the eccentricity, to generate between the two rollers a gap which is greater than the band thickness. After the completion of the clearance-generating process, the eccentric can be rotated in the then opposite direction again, whereby the two rollers clamp the band between them again and a band retraction process can be performed by way of the two rollers. Said embodiment of the present disclosure has inter alia the advantage that a fast movement of the counterpart roller for the generation of a spacing to the driven roller, and an advancing movement toward the driven roller again, are possible by way of an eccentric with a relatively small structural space requirement. In other embodiments of the present disclosure, the spacing between the two rollers for the clearance-generating process may self-evidently also be realized in some other way, for example by way of a pivoting movement or a linear movement of at least one of the two rollers.
- In a further expedient embodiment of the present disclosure, it may be provided that the clearance-generating movement is realized by way of a linearly movable driven element such as for example a stroke-performing piston. Such stroke-performing elements are available in a variety of forms and with different drive principles. With such stroke-performing elements, it is possible the drive movement to form particularly functionally reliable clearance-generating devices. Furthermore, with such drive elements, it is also possible with relatively little outlay for existing strapping apparatuses to be retrofitted with a clearance-generating device.
- A further embodiment of the present disclosure may provide, for the tensioning device, that, in the region of the circumferential surface of the tensioning wheel, there is provided on the tensioning wheel at least one movable spacer element which can be arranged in a first position and in a second position that differs from said first position, wherein, in the first position, the spacer element can be arranged at least in sections with a first spacing to the axis of rotation of the tensioning wheel and, in the second position, can be arranged with a second spacing, at least in sections, to the axis of rotation of the tensioning wheel, the first spacing differs here from the second spacing, and the spacer element, in at least one of the two positions, projects beyond the circumferential surface of the tensioning wheel. This embodiment thus makes it possible, by way of the at least one spacer element, for the strapping band to be prevented from coming into contact with the surface of the tensioning wheel when the spacer element assumes its position in which it projects at least in sections beyond the circumferential surface of the tensioning wheel.
- In a embodiment of the present disclosure, it may be provided that, by way of a force externally applied to the spacer element of the tensioning wheel, the spacer element can be transferred at least in sections from the position with the relatively large radial spacing to the axis of rotation into the other position with the relatively small radial spacing to the axis of rotation. The expression “externally applicable” may in this case be understood in particular to mean that the force is applied by an element which does not belong to the tensioning wheel or to the spacer element itself. The spacer element may be in the form of a passive element with regard to its change in position or the change in its geometrical shape. A structurally simple and nevertheless compact embodiment of the present disclosure may provide that the spacer element is arranged so as to be rotatable together with the tensioning wheel.
- It may be provided that the at least one spacer element assumes its first position during the band retraction phase, such that, during the band retraction phase, the strapping band is arranged against the at least one spacer element of the tensioning wheel and thus with a spacing to the circumferential surface of the tensioning wheel. The band is thus ideally prevented by the spacer element from coming into contact with the circumferential surface of the tensioning wheel during the band retraction phase. If such contact is not entirely avoidable, said contact should however at least be reduced to the greatest possible extent by the spacer element. For the tensioning phase or the tensioning process, it is by contrast possible, in certain embodiments of the present disclosure, for the at least one spacer element to be moved with at least one of its sections into the second position thereof in which, at those points of the circumferential surface at which the tensioning wheel is looped around by the strapping band, said at least one spacer element is arranged no higher than the same height as the circumferential surface, or is arranged lower than said circumferential surface. In this way, the spacer element leaves the circumferential surface free for the desired contact with the circumferential surface during the tensioning process.
- As a spacer element, both passive and active spacer elements may be provided for the purposes of moving the at least one spacer element into its two positions. Active elements may be understood as elements which perform a change in position or shape automatically, for example elements which perform self-generating changes in position and/or shape of the spacer element through the use of hydraulic or pneumatic energy or the use of electrical or magnetic energy. By contrast, however, certain embodiments include passive spacer elements, that is to say spacer elements which have a change in position and/or shape externally forcibly imparted to them, without the spacer element itself contributing to this. A change in position or shape may be realized for example by way of a counterpart roller which imparts a pressure force in the direction of the tensioning wheel and presses the band against the spacer element. In the presence of a correspondingly high force coordinated with the characteristics of the spacer element, it is possible in this way for the region of the spacer element to be provided with a smaller spacing to the axis of rotation of the tensioning wheel than in the unloaded state. The change in spacing may be utilized to the effect that, in the region of the counterpart roller, the strapping band bears now not against the spacer element but against the circumferential surface of the tensioning wheel.
- Another embodiment of the present disclosure may provide both a counterpart roller, which imparts force in the direction of the tensioning wheel, and the utilization of the band for generating the change in position. In this way, it is possible for the change in position and/or shape of the spacer element to be realized in a particularly functionally reliable manner. Here, it may be advantageous if, in particular at the start of the tensioning phase, the band is forced against the spacer element by way of a counterpart roller or some other suitable element and, in this way, the spacer element is, at least in the region of the counterpart roller, forced back such that the band comes into contact with the circumferential surface. In this way, the band enters into engagement with the tensioning wheel, whereby it is possible to commence with increasing the band tension. As a result of this, the band begins to lie against the spacer element over an at least substantially predetermined wrap angle corresponding to its provided band guidance around the tensioning wheel. By way of an increase of the band tension, it is then also possible for the pressure force to be increased to a magnitude sufficient to force the spacer element back in the region of contact with the band, in such a way that the band is, over its wrap angle on the tensioning wheel, in contact with the circumferential surface of said tensioning wheel. Here, it is particularly advantageous for the spacer element to be forced back to such an extent that the spacer element, at least over a part of the wrap angle (and in certain embodiments substantially over the entire wrap angle) does not project beyond the contact region of the circumferential surface with the band. It is thus possible for the tensioning wheel to remain in engagement by way of its non-smooth circumferential surface even in the presence of further increasing band tension, and the band tension can be increased up to an intended value.
- In this context, the expression “do not project beyond the circumferential surface” can also be understood to encompass arrangements in which the spacer element projects only slightly beyond the circumferential surface, and the strapping band, for example owing to its elasticity and deformability, can come into contact with the circumferential surface despite said small projecting length.
- In a further embodiment of the present disclosure, the circumferential surface of the tensioning wheel may, at least over a part of the length of the circumference, be equipped with a groove in which, as a constituent part of the spacer element, there may be arranged a ring element which can be arranged at least in sections in different positions. Here, the ring element may advantageously be arranged in a first position, in which it is elevated at least in sections in relation to the circumferential surface, and in a second position, in which the ring element, at least in sections, does not project beyond the circumferential surface.
- Basically, a multiplicity of different solutions is conceivable by way of which the spacer element, such as for example the ring element, prevents the strapping band from coming into contact with the surface, which is intentionally kept non-smooth, of the tensioning wheel. A particularly advantageous solution may provide that the ring element extends substantially over the entire circumference of the tensioning wheel and is arranged in a groove which extends over the circumference of the tensioning wheel. In an expedient refinement of the present disclosure, it may be possible for the ring element to be forced into the groove by the strapping band under pressure loading, such that, owing to the ring element being forced back in this way, it is the case along a wrap angle that the ring element no longer projects beyond the circumferential surface, and the strapping band can come into contact with the circumferential surface of the tensioning wheel. The ring element may be designed so as to be forced back into the groove in the described manner only under the action of a certain minimum force acting on the ring element. Said minimum force may be predetermined such that it is reached during the tensioning process but not during the band retraction process.
- In a further particular advantageous embodiment, it is possible for the ring element, or other embodiments of the spacer element, to be of resiliently elastic form, whereby said ring element immediately and automatically restores itself when correspondingly relieved of the band pressure after having previously been subjected to load. Aside from a high level of functional reliability, this solution also makes it possible to avoid a supply of external energy.
- Finally, in a further embodiment of the tensioning device, during the tensioning process, the tensioning wheel rotates and, in relation to a positionally static polar coordinate system of the tensioning wheel, the spacer element is forced into the groove at the at least substantially always identical circumferential section of the tensioning wheel, whereas, at the remaining circumferential section, against which the strapping band does not bear, the spacer element projects in relation to the circumferential surface.
- Further embodiments of the present disclosure will emerge from the claims, from the description and from the drawing. The content of disclosure of the patent claims is hereby incorporated by reference into the description. The present disclosure will be discussed in more detail below on the basis of exemplary embodiments which are illustrated purely schematically in the figures.
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FIG. 1 s a highly schematized illustration of a strapping apparatus according to the present disclosure which is equipped with a strapping head according to the present disclosure. -
FIG. 2 is a perspective illustration of a strapping head according to the present disclosure. -
FIG. 3 is a perspective illustration from above of the strapping head fromFIG. 2 integrated into a band guide of a strapping apparatus. -
FIG. 4 shows a side view of the strapping head fromFIG. 2 , in the case of which a component is situated in a pivoted-out servicing position. -
FIG. 5 is a perspective partial illustration of the strapping head fromFIG. 2 , with the band drive device being illustrated. -
FIG. 6 shows a front view of the band drive device fromFIG. 5 . -
FIG. 7 is a perspective illustration of a tensioning wheel according to the present disclosure with a partial illustration of the knurling of the circumferential surface of the tensioning wheel. -
FIG. 8 shows a front view of the tensioning wheel fromFIG. 7 . -
FIG. 9 is a cross-sectional illustration of the tensioning wheel along a diameter line. -
FIG. 10 shows a component of a lever mechanism for a counterpart roller of the band drive device. -
FIG. 11 shows a further component of the lever mechanism of the counterpart roller in a perspective illustration. -
FIG. 12 shows the component fromFIG. 11 in a front view. -
FIG. 13 is a sectional illustration of the component fromFIGS. 11 and 12 . -
FIG. 14 is an exploded illustration of a further exemplary embodiment of a tensioning wheel. -
FIG. 15 is a perspective illustration of the tensioning wheel fromFIG. 14 . -
FIG. 16 shows a front view of the tensioning wheel fromFIGS. 14 and 15 . -
FIG. 17 is a sectional illustration of the tensioning wheel fromFIGS. 14-16 . -
FIG. 18 shows a further exemplary embodiment of a band drive device according to the present disclosure with a clearance-generating device in a partial illustration of a strapping head. -
FIG. 19 shows the band drive device fromFIG. 18 in an illustration in which a clearance has been generated between a counterpart roller and the driven roller that interacts therewith. -
FIG. 1 shows a strappingapparatus 1 which is equipped with acontroller 2, asupply device 3 for storing and making available a strapping band, and with a strappinghead 5. The strappinghead 5 serves inter alia for the generation of an advancement movement and for the generation of a retraction movement of the strapping band. Said strapping head is furthermore equipped with a tensioning device, for imparting a band tension to a band loop, and a fastening device for generating a fastening on the strapping band. Furthermore, the strapping apparatus has aband guide 6 by way of which the band can be mechanically and automatically laid around a packaged item 7 on a predefined path. A welding and clampingunit 16 is also integrated into the strappinghead 5. Aside from the strappinghead 5, these are components that are known per se of strapping apparatuses. - The strapping
head 5, which is arranged together with theband guide 6 on aframe 8 and which is separately illustrated inFIG. 2 has aband drive device 15. Band drive devices are basically already known, for which reason substantially the differences in relation to previously known band drive devices will be discussed below. The band drive device according to this exemplary embodiment may be equipped in particular with one or more roller pairs 11, 12; 13 and possibly with further individual diverting rollers. The latter however do not participate in the generation of the band movement and are provided only for determining the band running direction. Of the threerollers rollers roller - The strapping
head 5 has two components: acontrol component 16 and aband handling component 17. In the exemplary embodiment, thecontrol component 16, aside from the execution of control functions for the components of the strapping device, has further functions, for example the generation of fastenings between the two belt layers of a strap and the cutting of the strapping band from the band supply. Thecontrol component 16 is in this case mounted on apartial carrier 18 of the strapping head, wherein thepartial carrier 18 is in turn detachably fastened to a common main carrier 19 of the strappinghead 5. As can be seen in particular fromFIG. 4 , thepartial carrier 18 of thecontrol component 16 is pivotable about an axis 23. The elements of theband handling component 17 are fastened, without a dedicated partial carrier, directly to the main carrier 19 of the strapping head. In the exemplary embodiment, thecontrol component 16 is provided substantially for performing control and coordination functions out of the functions performed by the strapping head. Theband handling component 17 and the components attached thereto are, by contrast, provided for acting directly on the strapping band. - A
band advancement device 20, aband retraction device 21 and atensioning device 22 are integrated into theband handling component 17 of the strappinghead 5. In the exemplary embodiment shown here,common rollers tensioning devices rollers rollers rollers motor 14, in the exemplary embodiment an electric motor. For this purpose, it may for example be provided that, from thecommon motor 14, in each case one drive train leads to one of the tworollers roller 11 is provided both as a drive wheel for the band advancement (band advancement wheel) and as a drive wheel for the band retraction (band retraction wheel). In order that, in the exemplary embodiment illustrated, said two functions can be performed by way of only one wheel, theroller 11 can be driven in both directions of rotation by thesame drive motor 14. Here, in the illustration ofFIG. 6 , the direction of rotation counterclockwise is the band advancement direction, and the direction of rotation clockwise is the band retraction direction. As shown inFIG. 2 , the motor drive movement is transmitted to both wheels orrollers common motor 14 by way of a mechanism device. In the present exemplary embodiment, the mechanism device 14 a comprises a toothed-belt mechanism which transmits the drive movement from the motor shaft to a further shaft running parallel to the motor shaft. On said further shaft there are arranged two gearwheels which belong in each case to a further one of two partial mechanisms of the mechanism device. One of said two partial mechanisms of the mechanism device transmits the motor drive movement to the roller or thewheel 11, and the other partial mechanism transmits the motor drive movement to thetensioning wheel 12. Depending on the direction of rotation of the motor shaft, it is thus the case in the exemplary embodiment that both thetensioning wheel 12 and thewheel 11 rotate in different directions of rotation. - In the installed position of the strapping head depicted in
FIGS. 5 and 6 , theroller 11 is arranged above theroller 12. Theroller 12 is a constituent part of thetensioning device 22 and has the function of the tensioning wheel. Said roller has a considerably greater diameter than theroller 11. Thetensioning wheel 12, owing to the rigid connection to themotor 14 and the drive movements in both directions of rotation performed by the motor, can likewise be driven in both directions of rotation. For the imparting of the intended band tension to the strapping band, in particular to the band loop, the tensioning wheel however utilizes only the drive movement in the tensioning direction, that is to say the clockwise direction of rotation as viewed in the illustration ofFIG. 6 . In certain embodiments, a release of tension from the band section which is situated in the strapping head, and which is no longer part of the band loop, may be realized by way of a rotational movement of the tensioning wheel, taking place after the tensioning process, in the direction of rotation opposite to that during the tensioning process. The drive movements both for the tensioning movement and for the tension-relieving movement originate from the same drive motor as for theroller 11. As an alternative to the exemplary embodiment of the present disclosure illustrated here, it is possible in other embodiments for a switchable clutch to be provided in the drivetrain (not illustrated in any more detail) from the motor to the tworollers roller 11 or to theroller 12. Aside from embodiments in which the tensioning wheel is in turn capable of being driven in both directions of rotation, it may also be provided that the tensioning wheel can also be driven only in the direction of rotation provided for the tensioning process. - As can be seen from the illustration of
FIG. 6 , theroller 13 is adjacent both to theroller 11 and to thetensioning wheel 12. Theroller 13 is not driven in rotation and is pivotably articulated by way of a pivoting device. The pivoting device is operatively connected to a drive by way of which the roller can perform (motor-) driven pivoting movements. By way of the pivoting movement, theroller 13 which functions as counterpart roller can be placed either in contact with theroller 11 or in contact with thetensioning wheel 12, wherein, in the respective end position of thepivotable roller 13, the strapping band is situated in each case between one of therollers roller 13. Depending on which of therollers counterpart roller 13 bears against, thecounterpart roller 13 then forces the band against the correspondingroller roller counterpart roller 13 is thus, together with theroller 11, both a constituent part of the band advancement device and a constituent part of the band retraction device. Together with thetensioning wheel 12, thecounterpart roller 13 is also a constituent part of thetensioning device 22. By way of this configuration according to the present disclosure, it is possible for the fourth roller that has hitherto been conventional in previously known solutions to be dispensed with. In the case of said previously known solutions, the drive roller and the tensioning wheel are in each case fixedly assigned one of two counterpart rollers. The 3-roller solution according to the present disclosure can permit a considerably more compact embodiment in relation thereto. - The
rollers head 5, furthermore a constituent part of aband guide channel 28 which predefines the profile and the advancement and retraction path of the band. Theband guide channel 28 is in turn part of theband guide 6. As can be seen inFIG. 6 , the strappinghead 5 has afirst interface 29 at which the strappinghead 5 adjoins the supply roll side of the band guide. That end of theband guide channel 28 which is formed here is in the form of a quick-change interface. This has achannel piece 31 which can be clamped to the strapping head by way of apivotable clamping lever 30 and through which the band is supplied into the strapping head. Thechannel piece 31 ends directly in front of thecircumferential surface 11 a of theroller 11, such that the strapping band can be supplied at least approximately tangentially to thecircumferential surface 11 a of theroller 11. If theroller 13 is situated in its end position in which it is pivoted toward theroller 11, the band is led through between therollers roller 13 forces the band against theroller 11. - As viewed in the
band advancement direction 32, the band passes, in its further progression, to thetensioning wheel 12. Here, proceeding from thecounterpart roller 13, a circular-arc-shapedchannel section 28 a which extends over approximately 180° of the circumference of thetensioning wheel 12 is formed by way of suitable channel-forming means. With regard to the band thickness, thechannel section 28 a is formed so as to be considerably wider than the band thickness. The inner delimitation of the channel section is formed by that section of thecircumferential surface 12 a of thetensioning wheel 12 which is situated in each case in the region of the channel section. The outer delimitation of thechannel section 28 a as viewed radially has guide plates and an outer channel segment which is pivotable together with thecounterpart roller 13, by way of which outer channel segment the outer channel section can be kept closed despite thepivotable counterpart roller 13 being situated in the region of the outer channel section. Without thepivotable channel segment 33 or some other element of similar action, there would possibly be an open point of the channel section at least in one of the two pivoting end positions of thecounterpart roller 13, which open point could possibly have an adverse effect with regard to reliable band guidance. -
FIGS. 7, 8 and 9 show the tensioning wheel in three illustrations. Said tensioning wheel has aring 37 which is equipped with arecess 38 which is provided for the connection of thetensioning wheel 12 to a shaft of the drive, in particular to a shaft of a mechanism of the drive.FIG. 2 shows thetensioning wheel 12 mounted on the shaft. As can likewise be seen fromFIG. 6 , the circular tensioning wheel has acircumferential surface 12 a with an at least substantially constant width. Thetensioning wheel 12 is equipped, on itscircumferential surface 12 a, with a knurling ortoothing 39 by way of which the engagement conditions of thetensioning wheel 12 on the strapping band are improved. Instead of a knurling ortoothing 39, it would also be possible for any other geometrically defined or undefined roughening of thecircumferential surface 12 a of the tensioning wheel to be provided, by way of which possible slippage between the tensioning wheel and the strapping band during the tensioning process can be at least substantially prevented. - A
groove 40 with a relatively small width is formed over the entire circumference of thecircumferential surface 12 a at least approximately centrally—in relation to the width of thetensioning wheel 12—and so as to be spaced apart from the lateral edges of the tensioning wheel, which groove is formed so as to be considerably deeper than it is wide. In the exemplary embodiment, two resiliently elastic O-rings groove 40, said O-rings being arranged radially one behind the other in thegroove 40. Here, one of the O-rings 43 is arranged with a relatively small spacing to the axis of rotation of thetensioning wheel 12, and the other O-ring 44 is arranged with a relatively large spacing to the axis of rotation of thetensioning wheel 12. The width of the O-rings groove 40. The two O-rings groove 40. The two O-rings - On the outer of the two O-
rings ring 45 which is provided as a spacer element and which, in the exemplary embodiment, is formed from a metallic material. In this exemplary embodiment, thering 45 is elastically deformable. It would likewise be possible for the ring to be of substantially rigid or dimensionally stable form. To realize said elastic characteristics of the ring, it would also be possible for thering 45 to be formed from one or more materials other than a metallic material, for example from an elastic plastic. In the exemplary embodiment, saidmetal ring 45 is, in terms of its cross section, provided so as to have a width B smaller than its height H. The height of the O-ring is, with regard to the groove depth and the height of the O-rings, configured such that the ring projects with a height H1 out of thegroove 40. Thus, in its unloaded state shown inFIG. 9 , thering 45 projects beyond thecircumferential surface 12 a of thetensioning ring 12, in particular over its entire circumference or over the entire circumference of thetensioning ring 12. - At the start of the strapping process, the strapping band is pushed at high speed, with its free band end first, from the strapping
head 5 through theband guide 6. For this purpose, thecounterpart roller 13 is in contact with one side of the band. The band is forced with its other side against the motor-drivenroller 11 by the counterpart roller. The rotational drive movement of theroller 11 in the advancement direction is in this way transmitted to the strapping band, which effects the advancement movement thereof in the advancement direction. Downstream of the region in which the band emerges from the gap betweenroller 11 andcounterpart roller 13, the band comes into contact with thetensioning wheel 12, but without exerting a significant pressure on thetensioning wheel 12. - After the band has been pushed all the way through the
band guide 6, the band end reaches the closure head again. Here, the band end actuates a limit switch, whereby the advancement movement is stopped and the band end is clamped. These and other activation and deactivation processes of components of the closure head are performed by thecontrol component 16 which, for this purpose, is equipped with a motor-driven camshaft control arrangement such as is basically known. - The camshaft control arrangement of the
control component 16 now sets theroller 11 in motion in a direction of rotation reversed in relation to the advancement direction. The strapping band, which remains clamped between theroller 11 and thecounterpart roller 13, is hereby moved in the reverse direction, that is to say in theband retraction direction 48. The circumferential length of the band loop, the band end of which remains clamped, is hereby continuously shortened. The band is hereby pulled out of theband guide 6 and, as a result, laid around the respective packaged item. -
FIG. 6 illustrates thetensioning wheel 12 during the band retraction process. As can be seen from said illustration, it is the case during the band retraction process that the band comes into contact with thetensioning wheel 12. The strapping band bears against thetensioning wheel 12 substantially over the entire circular-arc-shapedchannel section 28 a, similarly to the situation also encountered during the subsequent tensioning process. The band is duly retracted here, but, owing to its ability to yield to said movement by moving, as intended, out of the band guide, it is nevertheless the case during said phase that only a relatively low band tension is applied to the band of the band loop. As a result of said contact with thetensioning wheel 12 and of thering 45 which projects in relation to the circumferential surface, the band bears not against the circumferential surface of thetensioning wheel 12 but against thering 45 situated in thecircumferential surface 12 a. Said contact with the spacer element, which, in the exemplary embodiment, is in this case in the form of aring 45, has the effect that, during the band retraction, the band cannot be damaged by the knurling ortoothing 39 of thecircumferential surface 12 a. - After the band has been laid against the packaged article as a result of the band retraction, the controller switches from band retraction to generation of a band tension, whereby it is the intention for the band laid against the packaged article to be pulled taut. For this purpose, it is firstly the case that the
counterpart roller 13 is pivoted from its position of contact against theroller 11 into a position of contact against thetensioning wheel 12. Thetensioning wheel 12, which is rotated in the same direction of rotation as theroller 11 was previously, rotates at a lower rotational speed but with a greater torque, and pulls further on the strapping band. Owing to the absence of pressure of thecounterpart roller 13, it is by contrast now the case that the band no longer bears against theroller 11, which continues to be driven in the exemplary embodiment and which rotates at a higher speed, in such a way that theroller 11 could transmit its movement to the band. Since, at this stage, the strapping band already bears against the packaged article, the band is, by thetensioning wheel 12, retracted at most over a short length in relation to the band retraction phase. During said tensioning phase, it is in particular the case that a relatively high band tension is applied to the band. - Already at the start of the tensioning phase, the pressure of the
counterpart roller 13 in the direction of the tensioning wheel and the band situated in between causes thering 45 to be forced in the direction of the groove base and thus also in the direction of the axis of rotation of thetensioning wheel 12 as viewed in a substantially radial direction. In this way, it is the case already at the start of the tensioning phase that the band bears against thering 45 and forces the latter likewise, at least in the region of thecounterpart roller 13, in the direction of the groove base. Thus, already at the start of the tensioning process, thering 45 has, in the region of thecounterpart roller 13, a smaller spacing to the axis of rotation of the tensioning wheel than in its unloaded state, for example during the band advancement or the band retraction phase. - The torque transmitted from the
tensioning wheel 12 to the band during the further course of the tensioning process, which torque is higher than that in the band retraction phase of theroller 11, results in a greater reaction force of the band. Said greater reaction force now has the effect that the band forces thering 45 into the groove not only in the contact region with thecounterpart roller 13 but over its contact length (wrap angle as viewed in the circumferential direction) with thering 45, whereby the band now bears, along its wrap angle on thetensioning wheel 12, against the circumferential surface of said tensioning wheel. Along its wrap angle on the tensioning wheel, the band forces the ring into the groove counter to the spring forces of the O-rings. Depending on the characteristics of thering 45, said ring is deformed possibly elastically as a result, and, along that circumferential section in which the strapping band does not bear against the tensioning wheel, said ring can partially (with regard to its height) emerge from the groove again. Outside the wrap angle of the band on the tensioning wheel, thering 45 may in this case project out of the circumferential surface to a greater extent than in the unloaded state, in the case of which it projects with a height H1. Since the ring is arranged rotationally conjointly in the groove, it is the case, in a manner dependent on the respective rotational position of thetensioning wheel 12, that each individual point of the ring is forced into thegroove 40, and emerges from said groove again, in alternating fashion until, owing to the rotation of the tensioning wheel, said point arrives again at the point at which the band wraps around a section of the circumferential surface and thereby forces the ring into the groove along said section. It is thus possible, despite the means provided for preventing the strapping band from coming into contact with the circumferential surface of the tensioning wheel during the band retraction phase, for functionally reliable contact of the band with the same tensioning wheel to nevertheless be achieved during the band tensioning phase. - The
counterpart roller 13 can advantageously be forced with different pressing forces firstly against the roller 11 (advancement roller or retraction roller) and secondly against the tensioning wheel 12 (during the use of the strapping device in each case with a strapping band situated in between). Higher pressing forces against the tensioning wheel than the possible pressing forces against theroller 11 can be advantageous for high functional reliability and for the possibility of applying high band tensions to the strapping band. Therefore, below, it will be discussed how, in one embodiment of the present disclosure, despite the pivoting movement of thecounterpart roller 13 between two end positions, different pressing forces can be realized in the end position. - For this purpose, the
counterpart roller 13 is arranged on an eccentric 50 which, in turn, is arranged on ashaft 51 of acarrier 52. The carrier has, spaced apart from theshaft 52, areceptacle 53 which is provided for arrangement on thebearing point 54 of the roller 11 (FIGS. 5 and 6 ). Here, thereceptacle 53 is freely rotatable about its axis of rotation on thebearing point 54 of theroller 11 and can thus perform pivoting movements about its axis of rotation. - In the region of the
counterpart roller 13 and of theroller 11, there is provided a parallelogram which hasmultiple levers parallelogram 56 has a longvertical lever 57, ahorizontal lever 58 and a shortvertical lever 59. The parallelogram is pivotably articulated on the longvertical lever 57 and on the shortvertical lever 59. Thelevers curve 62, it is possible for a rotational movement to be transmitted to the longvertical lever 57, which rotational movement leads to the pivoting movement of thelever 57 about itspivot bearing point 60. In the illustration ofFIG. 12 , the pivoting movement of thelever 57 takes place clockwise. - In this way, at the articulation point of the short vertical lever, the
lever 58 also pulls said short vertical lever in the direction of thelever 57, whereby thevertical lever 59 is, in the illustration ofFIGS. 11 and 12 , likewise pivoted clockwise about itspivot bearing point 62. As a result, anoblique surface 64 formed on the shortvertical lever 59 pushes against a bearing 51 arranged on theshaft 51. As a result, the oblique surface performs a movement clockwise (in the illustration ofFIG. 12 ) and has the tendency to assume a horizontal orientation. As a result, thecarrier 52 performs a pivoting movement, whereby thecounterpart roller 13 is pivoted from its end position against theroller 11 in the direction of thetensioning wheel 12. - When it reaches the tensioning wheel, the counterpart roller bears against the tensioning wheel and can perform no further pivoting movement. The
lever 57 however pivots further, whereby thebearing point 65 of the eccentric 50 is moved counterclockwise in the direction of an L-shapedcarrier 66. After thebearing point 65 pushes against the L-shapedcarrier 65, the movement of thebearing point 65 stops, and said bearing point is situated at least approximately in a line with anupper bearing point 66, the axis ofrotation 67 of thecounterpart roller 13 and the axis of rotation 68 of thetensioning wheel 12. A spring element that has hitherto generated the pressing force of thecounterpart roller 13 is, as a result, no longer active. - A further movement of the
lever 57 during its pivoting movement now has the effect that thelever 59 can also perform no further movement, and therefore twoparts 58 a and 58 b of thehorizontal lever 58 are pulled apart. Aspring element 70 arranged between the twoparts 58 a, 58 b of the lever is hereby compressed, whereby the spring force thereof increases. This leads to a torque of thelever 59 about thepivot bearing point 61 with the lever arm of the spacing of thepivot bearing point 61 from the articulation point 71 of thelever 58 on thelever 59. As a result, theoblique surface 64 pushes, in the form of a torque about thepivot bearing point 61, against the bearing, which now leads to a pressing force of theroller 13 against the tensioning wheel. By way of a correspondingly dimensioned and designedspring element 70 and corresponding lever ratios, it is possible in this way to realize high pressing forces of theroller 13 against the tensioning wheel. - A restoration of the parallelogram can be realized by way of a
further spring 73 arranged on thepeg 72 of thelever 5. - Alternative embodiments of components and assemblies discussed above will be described below. Here, substantially only differences in relation to the corresponding components from
FIGS. 1 to 13 will be discussed. Where said embodiments include identical or similar configurations to those in the exemplary embodiment ofFIGS. 1 to 13 , these will not be discussed in any more detail below; the content of disclosure of the exemplary embodiments ofFIGS. 1 to 13 is however also incorporated by reference for the exemplary embodiments ofFIGS. 14 to 19 . -
FIGS. 14, 15, 16 and 17 illustrate a further embodiment of atensioning wheel 112 according to the present disclosure. Thetensioning wheel 112 may be divided longitudinally in terms of its width, approximately in the center, wherein the twoparts tensioning wheel 112 are detachably connectable to one another by way of suitable fastening elements, for example screws 114. In the region of said parting plane, which need not run in a flat manner, an encirclinggroove 140 is formed in theouter ring 137 of thetensioning wheel 112, which groove is open toward thecircumferential surface 112 a of thetensioning wheel 112 and is narrowed or decreased in size toward said circumferential surface. - One or more restoring elements may be arranged in the
groove 140. In the exemplary embodiment, as a restoring element, there are arrangedelastic ring sections 143, for example multiple resiliently elastic O-ring sections 143. Said ring sections are distributed in thegroove 140 at regular intervals with respect to one another, as is the case in the exemplary embodiment with a total of fourring sections 143. The restoringelements 143 are situated below one or more spacer elements. In the exemplary embodiment, only one spacer element 145, in the form of a closed ring, is provided. An outer diameter of the ring 145 arranged in the groove is in this case dimensioned such that, in the unloaded state of the ring 145, said ring projects with its outer circumferential surface beyond thecircumferential surface 112 a of thetensioning ring 112. The ring 145 is situated with its inner circumferential surface in the groove. The restoring elements are attached to the inner circumferential surface of the circular and substantially dimensionally stable ring 145. In other embodiments, it is also possible for a different number of spacer elements, and a different number of restoring elements, to be provided. - As a result of contact of the strapping band against the ring 145, and as a result of a certain minimum pressure force being exerted on the ring along a certain angle range along a section of the circumference of the tensioning wheel by the strapping band, it is possible for approximately that section of the ring 145 which projects beyond the groove along said angle range to be forced into the
groove 140, such that, in said positionally static angle range of thetensioning wheel 112, the strapping band comes into contact with thecircumferential surface 112 a of thetensioning wheel 112 and can be driven along by thecircumferential surface 112 a during the movement of thetensioning wheel 112. The ring 145, which substantially cannot be deformed by the expected forces acting thereon in the exemplary embodiment, and which is thus dimensionally stable, is thus arranged slightly eccentrically in relation to the axis of rotation of the tensioning wheel during said process. The ring 145 hereby projects, with its section not encompassed by the wrap angle of the band, out of thegroove 140 further than when the tensioning wheel is in the state in which it is not subject to load by the strapping band. As a result of the ring 145 being relieved of the load of the strapping band, or when a pressure force exerted on the ring 145 by the strapping band is not sufficient, it is possible, after the completion of the tensioning process, for the elastic restoring forces of one or more of thering sections 143 to cause the ring 145 to project out of the groove again over its entire circumference. - By way of this arrangement, it is possible, during the tensioning process, during which the tensioning band exerts an adequately high pressure force on the ring 145 situated in the wrap region of the strapping band, for the ring 145 to be forced in sections into the
groove 140. During the retraction process, during which only a relatively low tensile stress is present in the strapping band, the pressure force on that section of the ring 145 which is presently arranged in the wrap region of the band is not high enough to force said ring section entirely into thegroove 140. As a result, the band bears against the section of the ring 145 and not against the surface of thetensioning wheel 112. The ring 145 holds the strapping band so as to be spaced apart from the circumferential surface of thetensioning wheel 112. -
FIGS. 18 and 19 illustrate a further exemplary embodiment of aband drive device 115. Said band drive device also has only threerollers rollers rollers FIGS. 5 and 6 . - The
counterpart roller 113 is again designed to be pivotable, such that, in one pivoting position, it is provided for pressing the strapping band against theroller 111, and in another pivoting position, it is provided for pressing the strapping band against thetensioning roller 112. The pivoting mechanism, provided for this purpose, of thecounterpart roller 113, and the drive of said pivoting mechanism, may in principle be of the same design as in the exemplary embodiment ofFIGS. 1 to 13 . As in the exemplary embodiment ofFIGS. 5 and 6 , thecounterpart roller 113 is rotatably mounted on an eccentric 150, such that thecounterpart roller 113 performs a non-circular-arc-shaped movement during a pivoting movement from one of therollers other roller FIGS. 18 and 19 , a clearance-generatingdevice 180 is mounted on the eccentric 150 of thecounterpart roller 113, wherein the clearance-generatingdevice 180 is supported with acarrier 181 on the frame of the strappingapparatus 101. Thebearing point 182 of the clearance-generating device on the eccentric 150 is itself arranged pivotably on the eccentric, and is in the form of a C-shaped or fork-shapedelement 183 to thereby form a receptacle for one end of apiston 184.Said piston 184 is arranged in displaceable fashion in thecarrier 181 of the clearance-generatingdevice 180. In the illustration ofFIGS. 18 and 19 , the support point is situated immediately above theroller 111. Thecarrier 181 of the clearance-generating device is in this case likewise mounted in pivotable fashion. - In the exemplary embodiment shown, the clearance-generating
device 180 is equipped with a clearance-generating element which is provided for performing a controlled movement by way of which thecounterpart roller 113 is acted on in order for thecounterpart roller 113, in its pivoted edition against theroller 111, to be moved such that a clearance is generated, or to be lifted slightly. Thecounterpart roller 113, in its pivoted position at theroller 111, should, even after the generation of a clearance, be able to be placed against theroller 111 again, for example likewise by way of the clearance-generating device. In the exemplary embodiment, the clearance-generating element is in the form of asolenoid 186 which is arranged and mounted on the clearance-generatingdevice 180. Thesolenoid 186 can, by way of itspiston 184, perform a linear stroke movement along thelongitudinal axis 184 a of itspiston 184. As shown inFIGS. 18 and 19 , one end of thepiston 184 is arranged in the recess, which is open toward thecarrier 181, of the C-shaped or fork-shapedelement 183. The end of thepiston 184 and the recess of the C-shaped element may in this case be designed such that, during the clearance-generating movement, the end of thepiston 184 in the C-shaped element can move relative thereto. - Here, the extended
longitudinal axis 184 a of thepiston 184 runs at least approximately through the articulation point of the C-shapedelement 183. A stroke movement of thepiston 184 in the direction of thecounterpart roller 113 thus leads to a rotational movement of the eccentric about its axis of rotation. In the illustration ofFIG. 18 , the rotational movement takes place counterclockwise, as can be seen from a comparison of the twoFIGS. 18 and 19 . The rotational movement of the eccentric 150 in turn has the effect that the axis of rotation of thecounterpart roller 113 is displaced in parallel and a gap, or an enlarged gap, is formed between theroller 111 and thecounterpart roller 113. The width of the gap should in this case have a size greater than the thickness of the strapping band being processed in each case. As a solenoid, use may for example be made of the product GKb-32.06 from the company Isliker Magnete AG, CH-8450 Andelfingen. - On the
piston 184 there may be arranged a mechanical spring element, in particular at least onecompression spring 188. Saidcompression spring 188 is compressed, and thus braced in resiliently elastic fashion, during the movement of thecounterpart roller 113 from thetensioning roller 112 into contact with theroller 111. The electrically actuable magnetic stroke-performing piston is deactivated, and thus has no action, in this phase. During the stroke movement, thecompression spring 188 is at least partially relaxed and the spring force acts so as to assist the force imparted by the solenoid, by way of which force thepiston 184 is moved so as to generate a clearance between thecounterpart roller 113 and theroller 111. In other exemplary embodiments, in which the solenoid or some other restoring element alone provides a force high enough for the clearance-generating process. - During the production of the strap, it is the case—as already described—that, by way of the
roller 111 and thecounterpart roller 113 which bears against the former roller and clamps the band between the two rollers, the band is moved through theband guide channel 28 in a feed direction. When the strapping band reaches the region of the end of the band guide channel, as is illustrated by way of example in highly schematized form inFIG. 1 , the band strikes a stop, or the fact that the end of the band guide channel has been reached may be detected in some other way, for example by way of a light barrier. In this way, a signal is generated, by way of which the control of the strapping apparatus stops the motor drive movement of theroller 111 and—at least substantially at the same time—triggers the stroke movement of thepiston 184 of the solenoid. In other embodiments of the present disclosure, it is also conceivable for the stoppage of the drive movement of theroller 111 and the start of the clearance-generating process to have a time offset with respect to one another, that is to say for the stoppage of the drive movement to be performed before or after the start of the clearance-generating process. - As a result of the starting of the clearance-generating process, the
piston 184 deploys in the direction of the C-shapedelement 183 and, here, acts by way of its end on the C-shaped or fork-shaped element. Owing to its arrangement on the eccentric 150, the eccentric is rotated during the stroke movement of the piston. In the exemplary embodiment and in the illustration ofFIG. 18 , the rotational movement of the eccentric takes place through a rotational angle of less than 90° counterclockwise. The rotational movement takes place counter to the spring force of the pressure-exertingspring 190, which in this case is compressed and is likewise articulated on the eccentric 150. As a result of the rotational movement, a clearance is generated between thecounterpart roller 113 and theroller 111, that is to say thecounterpart roller 113 is lifted from theroller 111, and the spacing between the tworollers - In the case of generic strapping apparatuses, the strapping band, which is shot at high speed through the band channel of the
band guide 6, has the tendency, owing to the sudden and abrupt stoppage of the band, to form convolutions between therollers rollers counterpart roller 113 is generated, the band can, in particular immediately after the stoppage of the advancement, move freely counter to the advancement direction in the direction of the band supply to the extent required for that part of the band which is possibly excess in relation to the length of the band channel, and which causes the formation of convolutions, to move back in the band guide channel. The controller of the strapping apparatus can then subsequently deactivate the solenoid again. As a result, the solenoid is rendered inactive, whereby the pressure-exertingspring 190 can move the eccentric 150 back again counter to the previous direction of rotation, and thus move thecounterpart roller 113 into its position of contact with the band again, in which the band is clamped between theroller 111 and thecounterpart roller 113. The subsequent band retraction and tensioning process can be performed in the same way as in the embodiments of the present disclosure as perFIGS. 1 to 13 . -
List of reference designations 1 Strapping apparatus 2 Controller 3 Supply device 5 Strapping head 6 Band guide 8 Frame 11 Roller 11a Circumferential surface 12 Tensioning wheel 12a Circumferential surface of tensioning wheel 13 Counterpart roller 14 Motor 14a Mechanism device 15 Band drive device 16 Control component 17 Band handling component 18 Partial carrier 19 Main carrier 20 Band advancement device 21 Band retraction device 22 Tensioning device 23 Axle 27 Pivoting device 28 Band guide channel 28a Channel section 28b Outer delimitation 29 Interface 30 Clamping lever 31 Channel piece 32 Band advancement direction 33 Outer channel segment 37 Ring 38 Recess 39 Knurling/ toothing 40 Groove 43 O-ring 44 O- ring 45 Ring 48 Band retraction direction 50 Eccentric 51 Shaft 52 Carrier 53 Receptacle 54 Bearing point 56 Parallelogram 57 Long vertical lever 58 Horizontal lever 59 Short vertical lever 60 Pivot bearing point 61 Pivot bearing point 64 Oblique surface 65 Bearing point 66 Carrier 67 Rotary axle 68 Rotary axle 70 Spring element 71 Articulation point 72 Peg 101 Strapping apparatus 111 Roller 112 Tensioning wheel 112a Circumferential surface 112b Part 112c Part 113 Counterpart roller 114 Screw 115 Band drive device 137 Ring 140 Groove 143 Ring section 145 Ring 150 Eccentric 180 Clearance-generating device 181 Carrier 182 Bearing point 183 C-shaped element 184 Piston 184a Axis 186 Solenoid 188 Compression spring 190 Pressure-exerting spring B Width H Height H1 Height
Claims (16)
Applications Claiming Priority (7)
Application Number | Priority Date | Filing Date | Title |
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CH181/14 | 2014-02-10 | ||
CH182/14 | 2014-02-10 | ||
CH00182/14A CH709245A2 (en) | 2014-02-10 | 2014-02-10 | Strap application of a strapping device for strapping goods with a strapping band. |
CH00183/14A CH709246A2 (en) | 2014-02-10 | 2014-02-10 | Strap application of a strapping device for strapping goods with a strapping band. |
CH183/14 | 2014-02-10 | ||
CH00181/14A CH709244A2 (en) | 2014-02-10 | 2014-02-10 | Chuck a strapper for strapping goods with a strapping band. |
PCT/CH2015/000015 WO2015117256A1 (en) | 2014-02-10 | 2015-02-10 | Strapping apparatus |
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WO2015117257A1 (en) | 2014-02-10 | 2015-08-13 | Orgapack Gmbh | Strapping device having a strip feed device |
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IT201700005654A1 (en) * | 2017-01-19 | 2018-07-19 | Messersi Packaging Srl | Strapping machine with improved strap movement unit |
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2015
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- 2015-02-10 TR TR2019/05484T patent/TR201905484T4/en unknown
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CH709221A2 (en) | 2015-08-14 |
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CH709220A2 (en) | 2015-08-14 |
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ES2883950T3 (en) | 2021-12-09 |
EP3105129A1 (en) | 2016-12-21 |
PL3105129T3 (en) | 2019-07-31 |
EP3105126A1 (en) | 2016-12-21 |
WO2015117256A1 (en) | 2015-08-13 |
PL3105128T3 (en) | 2021-11-22 |
EP3105129B1 (en) | 2019-01-16 |
EP3105128B1 (en) | 2021-04-28 |
TR201905484T4 (en) | 2019-05-21 |
US10220971B2 (en) | 2019-03-05 |
WO2015117257A1 (en) | 2015-08-13 |
US20170015451A1 (en) | 2017-01-19 |
WO2015117255A1 (en) | 2015-08-13 |
PL3105126T3 (en) | 2018-11-30 |
EP3105126B1 (en) | 2018-07-11 |
US11312519B2 (en) | 2022-04-26 |
WO2015117254A1 (en) | 2015-08-13 |
US10513358B2 (en) | 2019-12-24 |
EP3105128A1 (en) | 2016-12-21 |
CH709219A2 (en) | 2015-08-14 |
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