STRAPPING DEVICE HAVING A PIVOTABLE ROCKER

Abstract

Various embodiments of the present disclosure provide a mobile strapping device for strapping packaged products using a loop of wrapping strap. The strapping device includes a tensioning device for applying tension to the strap and a connecting device for connecting two overlapping portions of the strap. The tensioning device includes a rotatable tensioning wheel and a tensioning plate. The tensioning wheel is supported by a rocker that is pivotable to change a distance separating the tensioning wheel and the tensioning plate. The mobile strapping device includes a motor that is operably connectable to the rocker or the tensioning wheel such that the motor causes pivoting of the rocker or rotation of the tensioning wheel when operating in a first direction of rotation. In various embodiments, gearing, including a plurality of planetary gear sets, is used to operatively connect the motor to the rocker and the tensioning wheel.

Claims

1. A strapping device comprising: a base comprising a tensioning plate; a rocker pivotable about a rocker-pivot axis from a first rocker position to a second rocker position; a tensioning wheel rotatable about a tensioning-wheel axis and pivotable with the rocker such that movement of the rocker from the first rocker position to the second rocker position moves the tensioning wheel away from the tensioning plate and movement of the rocker from the second rocker position to the first rocker position moves the tensioning wheel toward the tensioning plate; a sealing device; a spring imparting a spring force to the rocker that biases the rocker to the first rocker position; and an input device movable from a release position to an activated position to activate a motor operably connected to the rocker to pivot the rocker from the first rocker position to the second rocker position, wherein the spring forces the rocker from the second rocker position toward the first rocker position responsive to the input device being released from the activated position.

2. The strapping device of claim 1, further comprising the motor.

3. The strapping device of claim 2, wherein the sealing device comprises a friction-welding device comprising a weld shoe, wherein the friction-welding device is movable between a release position and a welding position.

4. The strapping device of claim 3, wherein the motor is operably connected to the friction-welding device and configured to move the friction-welding device from the release position to the welding position.

5. The strapping device of claim 4, wherein the motor comprises a drive shaft operably connected to the rocker such that rotation of the drive shaft in a first rotational direction causes the rocker to pivot from the first rocker position to the second rocker position.

6. The strapping device of claim 5, wherein the drive shaft is operably connected to the friction-welding device such that rotation of the drive shaft in a second rotational direction opposite the first rotational direction causes the friction-welding device to move from the release position to the welding position.

7. The strapping device of claim 6, further comprising a transmission mechanism operably connecting the drive shaft to the friction-welding device such that rotation of the drive shaft in the second rotational direction actuates the transmission mechanism to move the friction-welding device downward from the release position to the welding position.

8. The strapping device of claim 7, further comprising a lifting element operably connecting the drive shaft to the rocker such that rotation of the drive shaft in the first rotational direction causes the lifting element to move to impart a lifting force on the rocker to cause the rocker to pivot from the first rocker position to the second rocker position.

9. The strapping device of claim 8, wherein the lifting element is rotatable such that rotation of the drive shaft in the first rotational direction causes the lifting element to rotate to impart the lifting force on the rocker.

10. The strapping device of claim 9, wherein the lifting element comprises a ring gear.

11. The strapping device of claim 10, wherein the base comprises an abutment and the ring gear comprises an outer surface comprising a cam engaging the abutment.

12. The strapping device of claim 11, further comprising gearing operably connecting the drive shaft to the rocker, the gearing comprising the lifting element.

13. The strapping device of claim 12, further comprising one or more clamping elements movable from a first configuration to a second configuration to switch the gearing from a first state in which the gearing operably connects the drive shaft to the tensioning wheel so rotation of the drive shaft in the first rotational direction causes the tensioning wheel to rotate about the tensioning-wheel axis to a second state in which the gearing operably connects the drive shaft to the lifting element so rotation of the drive shaft in the first rotational direction causes the lifting element to rotate to impart the lifting force on the rocker and cause the rocker to pivot from the first rocker position to the second rocker position.

14. The strapping device of claim 13, wherein the one or more clamping elements prevent the ring gear from rotating when in the first configuration and do not prevent the ring gear from rotating when in the second configuration.

15. The strapping device of claim 8, wherein the lifting element is pivotable with the rocker.

16. The strapping device of claim 5, further comprising a lifting element operably connecting the drive shaft to the rocker such that rotation of the drive shaft in the first rotational direction causes the lifting element to move to impart a lifting force on the rocker to cause the rocker to pivot from the first rocker position to the second rocker position.

17. The strapping device of claim 4, wherein the motor is operably connected to the tensioning wheel and configured to rotate the tensioning wheel about the tensioning-wheel axis.

18. The strapping device of claim 17, wherein the motor is operably connected to the weld shoe and configured to oscillate the weld shoe.

19. A strapping device comprising: a base comprising a tensioning plate; a rocker pivotable about a rocker-pivot axis from a first rocker position to a second rocker position; a tensioning wheel rotatable about a tensioning-wheel axis and pivotable with the rocker such that movement of the rocker from the first rocker position to the second rocker position moves the tensioning wheel away from the tensioning plate and movement of the rocker from the second rocker position to the first rocker position moves the tensioning wheel toward the tensioning plate; a spring imparting a spring force to the rocker that biases the rocker to the first rocker position; an input device movable from a release position to an activated position to activate a motor to rotate a drive shaft operably connected to the rocker in a first rotational direction to pivot the rocker from the first rocker position to the second rocker position, wherein the spring forces the rocker from the second rocker position toward the first rocker position responsive to the input device being released from the activated position; and a friction-welding device comprising a weld shoe movable via rotation of the drive shaft in a second rotational direction opposite the first rotational direction from a release position downward to a welding position.

20. A strapping device comprising: a base comprising a tensioning plate; a rocker pivotable about a rocker-pivot axis from a first rocker position to a second rocker position; a tensioning wheel rotatable about a tensioning-wheel axis and pivotable with the rocker such that movement of the rocker from the first rocker position to the second rocker position moves the tensioning wheel away from the tensioning plate and movement of the rocker from the second rocker position to the first rocker position moves the tensioning wheel toward the tensioning plate; a friction-welding device comprising a weld shoe, wherein the friction-welding device is movable between a release position and a welding position; and a motor comprising a drive shaft operably connected to the rocker and the friction-welding device such that: rotation of the drive shaft in a first rotational direction pivots the rocker about the rocker pivot axis from the first rocker position to the second rocker position; and rotation of the drive shaft in a second rotational direction opposite the first rotational direction moves the friction-welding device downward from the release position to the welding position.

Description

[0021] Other embodiments of the present disclosure will emerge from the claims, the specification, and the drawing.

[0022] The present disclosure shall be explained more closely with the help of sample embodiments represented schematically in the figures. There are shown:

[0023] FIG. 1 a strapping device according to the present disclosure in a perspective representation;

[0024] FIG. 2 an exploded representation of the tensioning apparatus of the strapping device from FIG. 1 with the motor;

[0025] FIG. 3 a perspective representation of the tensioning and closure mechanism of the strapping device from FIG. 1;

[0026] FIG. 4 another perspective representation of the tensioning and closure mechanism of the strapping device from FIG. 1;

[0027] FIG. 5 an exploded representation of another sample embodiment of the tensioning apparatus of the strapping device from FIG. 1 together with the motor;

[0028] FIG. 6 a perspective representation of the tensioning and closure mechanism of the strapping device from FIG. 1;

[0029] FIG. 7 another perspective representation of the tensioning and closure mechanism of the strapping device from FIG. 1;

[0030] FIG. 8 a side view of the tensioning apparatus from FIG. 5, in which a rocker is located in a first pivot end position;

[0031] FIG. 9 a side view of the tensioning apparatus of FIG. 5, in which the rocker is located in a second pivot end position;

[0032] FIG. 10 a side view of the tensioning apparatus of FIG. 2, in which the rocker is located in a position with large pressing force against a tensioning plate;

[0033] FIG. 11 a side view of the tensioning apparatus of FIG. 2, in which the rocker is located in a position with less pressing force against a tensioning plate as compared to FIG. 10;

[0034] FIG. 12 a partial perspective representation of the tensioning and closure mechanism;

[0035] FIG. 13 a sectional representation of the tensioning and closure mechanism;

[0036] FIG. 14 a schematic diagram of the geometrical relations of a strapping device.

[0037] The strapping device 1 shown in FIGS. 1 and 2, being exclusively manually operated, has a housing 2, which encloses the mechanism of the strapping device and on which a handle 3 is fashioned for handling the device. The strapping device, moreover, is provided with a base plate 4, whose bottom side is provided for being placed on an object being packaged. All the functional units of the strapping device 1 are fastened to the base plate 4 and to the carrier connected to the base plate, not otherwise depicted.

[0038] With the strapping device 1, one can tension a loop of plastic strap B, not otherwise shown in FIG. 1, for example, one made of polypropylene (PP) or polyester (PET), which has previously been placed around the object being packaged, by way of a tensioning apparatus 6 of the strapping device. For this, the tensioning apparatus has a tensioning wheel 7, with which the strap B can be grasped for a tensioning process. The tensioning wheel 7 is arranged on a pivoting rocker 8, which can swivel about a rocker pivot axis 8a. The tensioning wheel 7, arranged with its axis of rotation at a distance from the rocker pivot axis 8a, can be moved by a pivoting motion of the rocker 8 about the rocker pivot axis 8a from one end position with a distance from a curved tensioning plate 9 arranged on the base plate 4 to a second end position in which the tensioning wheel 7 is pressed against the tensioning plate 9. By a corresponding motor-driven movement in the reverse direction of rotation about the rocker pivot axis 8a, the tensioning wheel 7 can be removed from the tensioning plate 9 and swiveled back to its starting position, such that the strap located between the tensioning wheel 7 and the tensioning plate 9 is released for removal.

[0039] During use of the indicated embodiment of tensioning device, two layers of the strap are situated between the tensioning wheel 7 and the tensioning plate and are pressed by the tensioning wheel 7 against the tensioning plate. By rotation of the tensioning wheel 7, it is then possible to provide a sufficiently large strap tension to the strap loop for packaging purposes. The tensioning process and the tensioning device and rocker 8 advantageously designed for this shall be explained more closely below.

[0040] After this, a welding of the two layers can be done in familiar fashion at a location of the strap where the two layers of the strap loop are superimposed on each other, by way of the friction welding device 12 of the strapping device. In this way, the strap loop can be permanently closed. In the sample embodiment shown here, the friction welding and separating mechanism 12 is actuated by the same only one motor M of the strapping device with which all other motor-driven movements are also performed. For this, in familiar manner, there is provided a not otherwise depicted freewheeling in the direction of transmission from the motor M to the places where the motorized driving movement occurs, which has the effect that the driving movement is transmitted in the particular desired rotary driving direction to the corresponding functional unit of the strapping device and no transmission occurs in the other particular rotary driving direction of the motor.

[0041] The friction welding device 12 for this is provided with a welding shoe 13, shown only highly schematized, which is moved by way of a transmission mechanism 14 from a position of rest at a distance from the strap to a welding position in which the welding shoe is pressed against the strap. The welding shoe pressed by mechanical pressure against the strap in this way and the simultaneously occurring oscillating movement of the welding shoe with a predetermined frequency melts the two layers of the strap. The locally plasticized or melted regions of the strap B flow into one another and after a cooldown of the strap B there is produced a connection between the two strap layers. Insofar as is necessary, the strap loop can then be separated from the supply roll of strap by way of a cutting device of the strapping devices 1, not otherwise depicted.

[0042] The infeed of the tensioning wheel 7 in the direction of the tensioning plate 9, the rotary driving of the tensioning wheel 7 about the tensioning axis 6a, the lifting of the tensioning wheel from the tensioning plate, the infeed of the friction welding device 12 by way of the transmission mechanism 14 of the friction welding device 12 as well as the use of the friction welding device 12 in itself and the activating of the cutting device occur by use of only a single common electric motor M, which provides each time a driving movement for these components of the strapping device. For the power supply of the motor M, a replaceable storage battery 15 is arranged on the strapping device, especially one which can be removed for recharging, which serves to store up electrical energy. A supply of other external auxiliary energy such as pressurized air or other electricity can be provided, but does not occur in the case of the strapping device per FIGS. 1 and 2.

[0043] As shown in FIG. 4, the strapping device according to the present disclosure provides for a tapping of the driving movement of the motor M at two places of its drive axis, either for the tensioning apparatus 6 or for the friction welding device 12. For this, the motor M can be operated in either of the two rotary directions. The shifting of the transmission of the driving movement to the tensioning apparatus 6 or to the friction welding device 12 is done automatically by a freewheeling arranged on the drive shaft of the motor M (and not otherwise shown) in dependence on the rotary direction of the drive shaft of the motor. In one rotary direction of the drive shaft, the driving movement is transmitted to the tensioning apparatus 6. Thanks to the freewheeling, the friction welding device 12 experiences no driving movement in this case. In the other rotary direction, the tensioning apparatus 6 has no driving movement and the friction welding device 12 is driven. No manual shifting is required in this embodiment for changing the direction of transmission of the motorized driving movement. Such freewheeling in connection with a strapping device is already known, and so it shall not be further discussed here.

[0044] As is likewise shown in FIG. 4, the motorized transmission of the driving movement to the friction welding device 12 and transmission mechanism 14 occurs by any suitable manner. This might be, for example, a toothed belt drive with a toothed belt closed into a ring. One of the two gears is arranged on the drive shaft of the electric motor M, the other one belongs to a gearing of the friction welding device 12, by which the motorized driving movement moves both the transmission mechanism 14 and the welding shoe 13 of the friction welding device 12. In this way, the welding shoe pressed against two overlapping layers of the strap can be placed in an oscillatory movement with predetermined frequency and amplitude, by which the two strap layers are locally melted in the region of the welding shoe and welded together by the subsequent cool down.

[0045] On the drive shaft of the motor, situated behind the toothed belt drive for the welding mechanism as seen from the motor M, there is a bevel gear 19, which belongs to a bevel gearing of the tensioning apparatus, as does a second bevel gear 20 meshing with it. On the same shaft where the second bevel gear 20 is arranged there is also located a first gear 21 of another toothed belt drive 22, which is furthermore led across a second gear 23. The first gear 21 of the toothed belt drive 22 is arranged on the shaft 24 firmly against rotation.

[0046] On the other end of the shaft 24 is mounted the rocker 8 of the strapping device, being part of the tensioning apparatus 6 and also carrying an upstream gearing from the tensioning wheel 7, in the present case a planetary gearing 26, for which suitable bearing sites can be provided on the rocker 8. The rocker 8 is shoved onto the shaft 24 such that the rocker 8 is arranged and supported so that the rocker 8 can pivot about the longitudinal axis of the shaft 8. The longitudinal axis of the shaft 24 is thus at the same time the rocker pivot axis 8a, about which the rocker 8 can swivel.

[0047] The planetary gearing 26 can be configured as a single or multiple-stage planetary gearing, in particular, a two or three-stage planetary gearing. From an end face of the gear 23 facing the tensioning wheel 7, there sticks out an externally toothed input sun gear 30 belonging to the planetary gearing 26, whose axis of rotation is identical to the axis of rotation 6a of the input gear 23. On a shaft of the gear 23 on which the sun gear 30 is also configured in the sample embodiment, a freewheeling 45 is provided, which only enables one rotary direction of the sun gears 30, namely, the rotary direction which is provided for the driving of the tensioning wheel. The sun gear 30 is led through a ring gear 27 and through a central recess of a planet carrier 25, which are likewise part of the planetary gearing 26. Looking from the input side of the planet gear, the planet carrier 25 is arranged behind the ring gear 27 on the axle of the planetary gearing 26 corresponding to the tensioning axis 6a. The planet carrier could also be configured as a clamping, coupling or spur gear.

[0048] The ring gear 27 has at its outer circumference a cam 27c, which engages with an abutment 46 secured to the base plate 4 of the strapping device. The internally toothed ring gear 27 is supported in this way so that the cam 27c can execute slight relative movements within its engagement with the abutment 46, for example, in a recess 46a of the abutment. Furthermore, the ring gear 27 has a ring-shaped shoulder 27a, on which a roller bearing 28 is arranged for the mounting of the planetary gearing 26.

[0049] The planet carrier 25, whose axis is aligned with the tensioning axis 6a, engages by its three planet gears 25b with an internal toothing of the input ring gear 27 of the planetary gearing 26. The planet gears 25b of the planet carrier 25 furthermore engage with the sun gear 30, from which they can obtain a driving movement and transmit it, appropriately stepped down, to the ring gear 27. Thus, given a rotationally fixed arrangement of the planet carrier 25, a rotational movement of the sun gear 30 can be converted into a rotational movement of the ring gear 27. In the sample embodiment, a first clamp 29 of a locking mechanism is configured as a pivoting cam, which can be brought into contact with a clamping surface 25a on the outer circumference of the planet carrier 25 or pivoted away from the clamping surface 25a with a spacing. The cam is arranged so that, upon contact of the cam with the clamping surface 25a by a rotation of the input planet carrier 25 in the rotary direction provided for the planet carrier 25, the clamping action is further intensified. By an infeeding of the cam onto the clamping surface 25a by a corresponding shifting movement, the planet carrier 25 can be blocked against rotation. By another shifting movement, the cam 29 can be moved away from the clamping surface 25a, thereby releasing the planet carrier 25 for rotational movements. The shifting movement can trigger a pivoting motion of the clamp 29 about a shift axis 143, which is produced by activating a button 44.

[0050] The sun gear 30 is furthermore arranged in the region of the axis of rotation 31 of a ring gear 32, whose nontoothed external surface 32a is coordinated with a second clamp 33. The axis of rotation 31 is identical to or aligned with the tensioning axis 6a. The clamp 33 interacting with the outer surface 32a can essentially be configured in the same way as the first clamp 29 as a shifting cam, which can move between two end positions, whereby in the one position the ring gear 32 is blocked against rotation and in the other position the ring gear 32 is released for rotational movements. Moreover, an internal toothing of the ring gear 32 engages with three planet gears 34, which are mounted at the end face of the following planet carrier 35, facing the ring gear 32. The planet gears 34 of the planet carrier 35 furthermore engage with the sun gear 30 of the input gear 23, which protrudes into the ring gear 32.

[0051] The locking device in the embodiment being described is configured so that always only one of the gears 25, 32 is clamped against rotation and the other gear 25, 32 is free for rotational movements. Thus, depending on the positions of the locking devices 29, 33, it is possible for a rotational movement of the gear 23 and the sun gear 30 to result in either a rotation of the planet carrier 35 about the tensioning axis 6a and axis of rotation 31 by virtue of a movement of the planet gears 34 in the internal toothing of the ring gear 32. Or the rotation of the sun gear 30 depending on the positions of the locking device results in a rotation of the ring gear 32. If the planet carrier 25 is not clamped by the locking mechanism, the rotating sun gear entrains the planet gears 25b so that the planet carrier 25 rotates and the ring gear 27 remains stationary. On the other hand, if the ring gear 32 is not clamped, a rotation of the sun gear 30 results in an entrainment of the planet gears 34, which in turn set the ring gear 32 in a rotational movement. Since the resistance to rotation in the further course of the planetary gearing 26 is greater toward the tensioning wheel 7 than the torque needing to be overcome in order to set the ring gear 32 in rotation, the ring gear 32 will primarily rotate in this case and the tensioning wheel 7 at least for the most part will not rotate.

[0052] At the other end face of the planet carrier 35, turned toward the tensioning wheel 7, there is arranged rotationally firm on the planet carrier 35 another sun gear 36, which meshes with planet gears 41 of another planet carrier 42. A further sun gear 43 directed toward the tensioning wheel 7 and connected rotationally firm to the planet carrier 42 is led through a recess of the additional planet carrier 37, configured as a ring gear. The sun gear 43 stands in meshing engagement with planet gears 38 of the additional planet carrier 37, facing the tensioning wheel 7 The planet gears 38 of the second planet carrier 37 mesh in turn with an internal toothing of the tensioning wheel 7 and drive the latter in its rotational movement about the tensioning axis 6a. This rotational movement of the tensioning wheel 7, provided with a fine toothing on its external circumferential surface, is utilized to grasp the strap B with the circumferential surface and pull back the strap of the strap loop, thereby increasing a strap tension in the strap loop.

[0053] The third planet carrier 37 has a shoulder 37a on its outer surface, which can be brought into contact against a stop element 39 by a rotational movement. The stop element 39 itself is fixed not to the rocker, but to the base plate 4 or some other carrier, which does not participate in the pivoting motion of the rocker 8. Thus, the stop element 39 is stationary in regard to the shoulder 37a.

[0054] In use when strapping packaged goods, the strapping device 1 behaves as follows: after a loop of a customary plastic strap has been placed around the particular packaged goods, this is placed inside the strapping device in the region of the end of the strap where the strap loop is double-ply for a certain length, and the end of the strap is secured in the strapping device by a strap clamp, not otherwise depicted. A section of the strap B immediately next to the strap loop is placed in double layer on top of the tensioning plate 9 of the tensioning apparatus 6. The rocker 8 with the tensioning wheel 7 and the upstream gearing 26 is situated in its upper end position, in which the tensioning wheel 7 is arranged at a spacing (by its greatest design spacing) from the tensioning plate 9, so that the largest possible opening gap is produced, enabling an easy, comfortable and thus also rapid placement of the strap in the tensioning apparatus. After this, the rocker is lowered onto a tensioning plate 9 opposite the tensioning wheel 7 and pressed against the strap arranged between the tensioning plate 9 and the tensioning wheel 7. Both this transfer movement of the tensioning wheel and the magnitude of the pressing force exerted on the strap by the tensioning wheel at the start of the tensioning process can be produced in the described embodiment of the present disclosure by one or more prestressed spring elements 44 (not shown). By activating a button 10, the spring element can be released and the entire strapping process triggered with its consecutive steps of “tensioning”, “closing”, “cutting”, releasing the tension of the strap in the region of the tensioning apparatus, and “lifting of the rocker”, for which no further intervention by the user of the strapping device need occur.

[0055] After the tensioning wheel 7 is moved automatically from the open position to its tensioning position (see the tensioning position in FIG. 10 and the open position in FIG. 11), where the tensioning wheel 7 lies on the strap B and presses across the strap on the tensioning plate 9, the motorized driving movement is transmitted to the tensioning wheel 7. Now the second clamp 33 is moved into its position in which the second clamp 33 presses against the ring gear 32. The ring gear 32 is thereby arrested from rotational movements and locked. The first clamp 29, on the other hand, continues to be positioned at a spacing from the input planet carrier 25 and releases the ring gear 27 for rotational movements. The motorized driving movement, which thanks to the particular designated rotary direction of the motor M is transmitted via the bevel gearing 19, 20, 21 to the second toothed belt drive 22 and thus to the gear 23, goes from here in the sequence of the following mentioned gearing elements via the input gear 23, the sun gear 30, the planet gears 34, the sun gear 36, the planet gears 41, the sun gear 43 and via the planet gears 38 to the tensioning wheel 7. The tensioning wheel 7 can be driven by the multistage planetary gearing in greatly stepped-down rotational movement of the motor—and thus when necessary with correspondingly high torque—in the predetermined rotary direction.

[0056] In the just described “tensioning” operating state of the strapping device, the driven tensioning wheel 7 in engagement with the strap produces a corresponding, oppositely directed counterforce on the tensioning wheel 7, depending on the resistance resulting from the strap tension and acting on the tensioning wheel 7. This counterforce acts in the reverse direction of transmission of the motorized driving movement on all gearing elements of the multistage planetary gearing that are involved in the transmission of the driving movement. If a different type of gearing from a single or multiple-stage planetary gearing is used, the counterforce resulting from the already applied strap tension and put into the respective gearing via the contact with the tensioning wheel is also available for use in accordance with the present disclosure. According to the present disclosure, this counterforce can be used to improve the conditions of the process, especially the functional safety even when the applied strap tension is high. Thus, in order to use this counterforce for the following described purpose, it would be possible in theory to use each of these gear elements for this, in particular, to pick off and employ the mentioned counterforce at each of these gear elements.

[0057] In the sample embodiment, the planet carrier 37 is used for this. The planet carrier 37 is buttressed in this case via the stop element 39 against the base plate 4, so that the entire tensioning apparatus 6 is pressed about the rocker axis 8a against the strap in proportion to the force of resistance (strap tension). The tensioning wheel 7 is thus pressed against the strap B proportionally to the strap tension. The strap tension generated by the tensioning process is utilized in advantageous manner to increase the pressing force of the tensioning wheel 7 on the strap B as the strap tension increases steadily, so that the danger of a “slip-through” or a slippage of the tensioning wheel 7 during the tensioning process, which also increases with increasing strap tension, can be counteracted.

[0058] For this, the planet carrier is configured with the engaging element 37a, which interacts with the stationary stop element 39. The engaging element, configured as a cam and arranged on the outer circumference of the planet carrier and projecting essentially radially from it, is buttressed against the stop element 39. As can be seen from FIG. 3, for this purpose the stationary stop element 39 is located in the region of the head end of the strapping devices. The stop element 39 in the sample embodiment shown is situated on one side, namely, the head end, of the tensioning axis 6a and the rocker pivot axis 8a running essentially parallel to it is on the other side of the tensioning axis 6a. The rocker 8, on which the planet carrier 37 is arranged via a roller bearing and able to rotate about the tensioning axis 6a, is also able to swivel at least during the tensioning process, i.e., it is not blocked against pivoting motions but instead released for these. Furthermore, the planet carrier 37 is able to rotate during the tensioning process about the tensioning axis 6a. The strap tension created in the strap B as a reaction to the tensioning process brings about a force on the tensioning wheel 7 which is opposite the rotary direction of the tensioning wheel provided during the tensioning process. This reaction force acts from the tensioning wheel via the planet carrier 37 on the rocker 8 as a torque directed about the rocker pivot axis 8a, by which the planet carrier 37 is pressed with increased force against the strap in the direction of the tensioning plate 9. The higher the strap tension already produced in the strap, the higher the torque resulting from this and from the motorized driving movement continuing to act on the tensioning wheel 7. This torque, arising as a reaction, is in turn proportional to the resulting pressing force acting from the tensioning wheel 7 on the strap B, with which the strap B is pressed by the tensioning wheel 7 against the tensioning plate 9. Therefore, in the present disclosure, an increasing strap tension from the motorized driving movement on the tensioning wheel 7 goes hand in hand with an increasing pressing force of the tensioning apparatus on the strap.

[0059] After the ending of the tensioning process and the following welding process to form the closure and also after a motorized driven cutting process by a cutting device, not otherwise depicted, integrated in the strapping device, a quick and uncomplicated removal of the strap from the strapping device should be possible. To accomplish this, there is provided a motorized lifting movement of the tensioning wheel 7 from the clamping position. For this, the button is activated and for as long as the button 10 is activated the rocker also remains in the open position, in which a sufficient spacing is created between the tensioning plate 9 and the tensioning wheel 7. By releasing the button 10, the rocker is closed, for example, by spring force.

[0060] In the sample embodiment, to accomplish this at first the operative connection between the electric motor M and the tensioning wheel 7 is released and an operative connection is created between the electric motor M and the rocker 8. This is accomplished by switching the clamps 29, 33. The previously existing clamping of the ring gear 32 is lifted in that the second clamp 33 is removed from the outer surface 32a of the ring gear 32 and in this way the ring gear 32 is released for rotational movements. Basically at the same time or shortly thereafter, the first clamp 29 is lowered onto the clamping surface 25a of the planet carrier 25 and brought to bear against it in clamping fashion. In this way, the input planet carrier 25 is fixed and locked against a rotational movement about the tensioning axis 6a, along which the entire planetary gearing is situated.

[0061] In this way, the tensioning wheel 7 can turn freely without being driven and no longer has an operative connection to the electric motor M or the sun gear 30, such as might transmit a driving movement. A driving movement of the electric motor M with the same rotary direction as during the tensioning process is now utilized, thanks to the locking of the input planet carrier 25 of the planetary gearing, so that the planet gears 25b of the spur gear 25 entrain the input ring gear 27 in their rotational movement. The input ring gear 27 thus executes a rotational movement by virtue of the rotating planet gears 25b. The bearing and abutment of the ring gear 27 on the abutment element 46 leads to a pivoting motion of the ring gear 27 about the rocker axis 8a. The input ring gear 27, which is also connected rotationally firm to the rocker 8 thanks to the clamping, entrains the rocker 8 during this movement. This results in a lifting of the rocker 8 and the tensioning apparatus 6 secured to it, including the tensioning wheel 7. The rotational movement of the rocker 8 can be limited by an end stop or an end position sensor, which shuts off the motor M after reaching an end position in the opened position of the rocker 8 and triggers an arresting of the rocker. Thanks to the motorized lifting movement of the rocker 8 against the direction of action of the spring element 44, the spring element 44 also is once more provided with a greater prestressing force. The strap B can now be removed from the strapping device 1.

[0062] The strapping device is now ready for a new strapping process, which can occur in the same way as the previously described strapping process. In order to lower the rocker 8 after introducing a new piece of strap B in the strapping device 1, the spring element 44 must be released again, which can be done for example via an operator button on the strapping device . In the sample embodiment, the previously actuated button 10 is released for this. The spring force then swivels the rocker, now in the opposite direction, against the tensioning plate and clamps the strap for the next tensioning process with an initial pressing force between the tensioning wheel 7 and the tensioning plate 9. The variable pressing force in the rest of the tensioning process increases in the manner described.

[0063] In FIGS. 5 to 9 is shown another sample embodiment of a strapping device according to the present disclosure. In regard to its external appearance, this can also correspond to the representation of FIG. 1. The basic layout of this embodiment of the strapping device can also correspond to that of the previously discussed embodiment of the present disclosure. Accordingly, in this embodiment as well, only a single motor M is used, which is provided to drive the welding mechanism 12 and separating mechanism (not shown in FIG. 5) in one of the two directions of rotation of the motor on the one hand and the tensioning apparatus 6 on the other hand in the other direction of rotation of the motor. The optional driving of either the welding mechanism and separating mechanism on the one hand or the tensioning apparatus 6 on the other hand is done via a freewheeling and different directions of rotation of the motor M.

[0064] The embodiment likewise shows a pivoting rocker 80 of the tensioning apparatus 86, driven by motor about a rocker pivot axis 80a. In contrast with the previously explained sample embodiment, here it is not the tensioning wheel 87 but instead the tensioning plate 89 which is arranged on the pivoting rocker 80, whose rocker pivot axis 80a runs parallel to the tensioning axis 86a. The motorized driving movement with the direction of rotation which is used for rotational movements about the tensioning axis 86a is also used in this sample embodiment for the pivoting motion of the rocker 80. The rocker pivot axis 80a in this embodiment as well runs essentially parallel to the tensioning axis 86a, about which the tensioning wheel can rotate. The rotational movement of the motor is transmitted, behind a point at which the motorized driving movement is utilized for the welding mechanism, across a bevel gear pair 99, 100 to a planetary gearing 106 and from this it goes further to the tensioning wheel 87. A freewheeling 125 arranged on the shaft of an input sun gear 110 ensures that the input side of the planetary gearing 106 can only turn in one rotary direction. The planetary gearing 106 is provided with gear elements which can be optionally arrested by way of a locking mechanism having two clamps 29, 33, as in the previously described sample embodiment, so that the driving movement can be transmitted either to the tensioning wheel 87 or to the rocker 80.

[0065] In order to open the tensioning apparatus 86, the ring gear 107 is released via the locking device, i.e., the clamp 33 is not in clamping engagement with the ring gear 107. The tensioning wheel 87 can in this way turn freely without an operative connection with the motor M. Optionally, strap tension still acting on the tensioning wheel 87 from the strap B from the previous tensioning process is released in this way by the tensioning wheel 87 and the gearing 106 upstream from the tensioning wheel. With the clamp 29, the spur gear configured as a planet carrier 105 is locked, and its axis of rotation is aligned with the tensioning axis 86a, i.e., the axis of rotation of the tensioning wheel 87. The motorized driving movement transmitted from the bevel gear 100 to the input sun gear 110, thanks to the removable rotary arresting of the planet carrier 105 performed by way of the clamp 29, does not lead to a rotation of the planet carriers 105 but instead to rotational movements of the planet gears 105b of the planet carrier 105. The internal toothing of the ring gear 109 which engages with these planet gears 105b places the latter in rotational movement. As is especially seen in FIG. 7, an external toothing 109c of the ring gear 109 engages with an external toothing 150c of a circular arc segment 150, which is disposed stationary on one end of a connection shaft 151. The connection axis 151a of the connection shaft 151 runs parallel to the stationary tensioning axis 86a of this sample embodiment. Instead of the two external toothings 109c, 150c, the ring gear 109 could also be braced by a cam against an abutment element, in which case either the cam or the abutment element is neither fastened to the ring gear 109 nor movable in design and the other of the two elements should be disposed on the ring gear 109.

[0066] The rotational movement of the ring gear 109 and the engagement of the ring gear 109 with the circular arc segment 150 results in a rotational movement of the connection shaft 151 about the connection axis 151a. A spur gear 152 arranged at the other end of the connection shaft 151 engages with an external toothing 117c of the planet carrier 117 and in this way transmits the rotational movement about the connection axis 151a to the planet carrier 117. In relation to the tensioning axis 86a, the connection axis 151a is situated on one side and the rocker pivot axis 80a on the other side of the tensioning axis 86a, the rocker pivot axis 80a being located on the side of the head end of the strapping device.

[0067] The planet carrier 117 belongs to the drive train provided for the driving movement of the tensioning wheel 87. The operative connection of this drive train to the motor M is momentarily broken thanks to the above described shifting process of the locking mechanism. Thus, at the above-described moment in the process there is no operative connection of the motor M with the tensioning wheel 87 to drive the latter. As a result of the rotary movement transmitted to the planet carrier 117, the planet carrier 117 rotates about the tensioning axis 86a and entrains a dog 80c of the rocker 80 by a cam 117a arranged on its outer circumferential surface. As a result, the rocker 80, appearing as an arc in plan view, is rotated and opened.

[0068] The rocker 80, able to turn about the rocker axis 80a and having the approximate shape of an arc segment, is arranged with its lower free end underneath the tensioning wheel 87, so that the tensioning plate 89 arranged in the region of the free end of the rocker 80 can likewise be arranged directly beneath the tensioning wheel 87. In order to arrange the tensioning plate 89 with a spacing from the tensioning wheel 87, the previously described motorized driven movement of the rocker 80 is used in the rotary direction along arrow 112 (FIG. 6), by which the rocker 80 is opened as described and a spacing between the tensioning wheel 87 and the tensioning plate 89 is increased. The opening movement can be limited by an end stop. The motor-opened rocker 80 now enables a removal of the tensioned and closed packaging strap from the strapping device. After the finished strapping is removed, the end of a new strapping loop for the next tensioning process can be introduced between the tensioning plate and the tensioning wheel. The rocker 80 can be brought back once again to the tensioning wheel by the restoring force of the spring element 124 previously stretched during the opening movement and press the strap against the tensioning wheel with an initial pressing force for the tensioning process. In order to utilize the spring force and thereby move the rocker 80 in a rotary direction along arrow 113 in the direction of the tensioning wheel 87, an activation of a button or some other activating element can be provided, by which the spring force is released to act on the rocker. This can also involve a releasing of the button 10.

[0069] In order to tension the strap B arranged between the tensioning wheel 87 and the tensioning plate 89, the ring gear 107 is clamped on its outer circumferential surface by way of the clamp 33 to prevent rotational movements. The planet carrier 105 is not clamped, and so it can turn, as can the connection shaft 8. The motorized driving movement from the sun gear 30 in the planetary gearing 106 arranged on the tensioning axis 86a is transmitted through the planet carrier 105 and the ring gear 107 to the planet gears 114 of the second planet carrier 115 and sets the latter in rotation. A sun gear, not recognizable in the representation of FIG. 5, drives the planet gears 121 of an additional downstream stage of the planetary gearing 106. The planet carrier 122 of this stage also rotates. The sun gear 123 of the last-mentioned stage is further led through the additional planet carrier 117 and drives the planet gears 118 of this additional stage, which in turn are in engagement with an internal toothing of the tensioning wheel 87. The tensioning wheel 87 is thus driven in the tensioning direction across the single or multiple-stage planetary gearing 106 and the inserted strap B is tensioned.

[0070] In the previously described operating mode of “tensioning”, in which the tensioning wheel 87 engages with the strap B, a force of resistance in the form of a restoring moment acting from the strap B on the rotating tensioning wheel 87 is produced by virtue of the strap tension. Its magnitude is variable and proportional to the magnitude of the applied strap tension. This force of resistance works opposite the motorized driving moment which arises in the gear elements participating in the transmission of the driving movement. In the sample embodiment, the planet carrier 117 is braced by a cam 117b, having the function of an end stop, against the rocker 80. The planet carrier 117 rotating by the motorized driving movement in a suitable rotary direction lies by its cam 117b against a dog 80b of the rocker and thereby turns it in a motion according to arrow 113 (FIG. 6) about the rocker axis 80a against the tensioning wheel. Optionally, a noticeable rotary movement about the rocker axis 80a will not actually be executed here, but essentially only the torque about the rocker axis 80a is increased. In either case, however, the pressing force by which the rocker 80 presses the tensioning plate 89 or the strap against the tensioning wheel 87 is increased. This increase generally does not occur in a single step. The increasing of the pressing force of the rocker against the strap, ultimately stemming from the motorized driving movement and the already existing strap tension and occurring by engaging with the tensioning gearing 106, occurs proportionally to the resistance and restoring force present in the strap and acting as a resistance force against a maintaining and a further increasing of the strap tension at the point of engagement with the strap, from the strap to the tensioning plate 89 and on the tensioning wheel 87. As long as an increasing of the strap tension is occurring by the tensioning process, so too will the resistance force increase and thus the pressing force resulting from it.

[0071] In FIGS. 8 and 9 are shown the end positions of the rocker 80 which are possible on account of the swiveling ability of the rocker to open and close on the one hand and to increased the pressing force on the strap on the other hand. As shown in FIG. 8, in one of the two end positions the tensioning plate 89 by virtue of a contacting of the cam 117b of the planet carrier 117 with a contour of the dog 80b and a clockwise rotational direction of the planet carrier (in relation to the representation shown in FIG. 8) rotates the rocker counterclockwise about its rocker pivot axis. The dog 80b and the cam 117b in this case act like a lever, which produces a counterclockwise torque about the rocker pivot axis 80a.

[0072] FIG. 9 shows the end position of the opened rocker. Here, the planet carrier 117 turns in the opposite rotary direction as compared to FIG. 8 and thereby comes to bear against the dog 80c of the rocker 80. The dog 80c is situated in regard to the rocker pivot axis 80a and the other dog 80b on the other side of the rocker pivot axis 80a. In the position of use of the strapping device with a horizontal orientation of the base plate, the dog 80b is situated above and the dog 80c below the rocker pivot axis 80a. In this way, the rocker swivels clockwise in the representation of FIG. 9 and thereby creates a spacing from the tensioning wheel 87.

[0073] FIG. 12 shows a partial perspective view of the tensioning apparatus of the second sample embodiment, in which only one of the two clamps is depicted. Here, the clamp 33 is brought to bear against the flat circumferential surface 107b of the ring gear 107, which is essentially round in cross section. FIG. 13 shows a sectional representation through the ring gear 107 and the clamp 33. By way of the clamp 33 of the locking mechanism, the ring gear can be optionally clamped against rotational movements or released again. Each of the clampings provided in the strapping devices of FIG. 2-11 can be configured according to the locking mechanism described here, however traditional locking mechanisms are also possible. In the clamping according to the present disclosure, an at least approximately planar circular or circular arc-shaped circumferential surface of the gear interacts with a pivoting clamping element or clamping body. The circumferential surface 107b of the sample embodiment shown, functioning as a clamping surface, has no detent elements with which a clamping is provided that is based on a form-fitting engagement of a clamping element with a detent element or a detent recess.

[0074] The clamping element 33 is mounted so that it can pivot about the shifting and pivoting axis 143, where the shifting axis 143 of the clamping element 33 runs parallel to the axis of rotation of the gear 107 being clamped. The shifting axis 143 runs in the region of one end of the camlike clamping element 33. In the region of the other end of the clamping element there is provided an arc-shaped contact surface 33a, which is provided for a contact with the clamping surface 107b of the gear being clamped. Due to the circular shape of the clamping surface 109b as well as the arc shape of the contact surface 33a in side view, an essentially linear contact comes into being when the clamping element 33 contacts the circumferential surface 107b, and this line of contact runs perpendicular to the plane of the drawing in FIG. 13.

[0075] As emerges from FIG. 13, the clamping element 33 is arranged in relation to the gear 107 being clamped such that the line of contact of the contact surface 33a has a distance 155 from its pivot axis 143 which is greater than the distance of the pivot axis 143 from the clamping surface 107b. As a result, during a pivoting motion of the clamping element 33 from its release position to a clamping position it already comes into contact with the clamping surface 107b at a point which lies before a line of connection 156 of the axis of rotation of the gear 107 to the pivot axis 143 of the clamping element. In relation to the intended rotary direction 157 of the gear 107 being clamped, the line of contact occurs before the (imaginary) line of connection 156. The rotation of the gear 107 is braked and can at most still move just a little. Thanks to a further rotation against the increasing clamping action, the clamping action is further intensified and an increasing wedging of the clamping element 33 against the gear 107 is intensified. Thanks to these geometrical relations, the clamp 33 cannot pass the line of connection 156 in rotary direction of the gear, its pivoting motion halts before the line of connection 156 and presses against the clamping surface 107b. In an end position essentially corresponding already to the position of first contact with the clamping element 33, the gear 107 is clamped against the camlike clamping element 33. No further movement is possible, regardless of how high the torque is.

[0076] FIG. 14 shows the geometrical relations of the clamping. Here as well, the connection between the axis of rotation 86a of the gear 107 and the pivot axis 143 is designated as 156. The contact surface (circumference) of the gear could be smooth or structured. The radius of the gear at the contact site with the cam is designated as 158 and the pivot radius of the clamping element 33 at the contact site is 155. The pivot radius 155 at the contact site subtends an angle a with the line of connection 156, and the radius 158 of the gear 107 an angle y with the swivel radius 155 (each time at the contact site). In the sample embodiment, the geometrical relations are such that in the clamping position, in which the gear 107 is blocked against rotational movements in the intended rotary direction, the angle γ is at least approximately 155°. In experiments it was also possible to achieve good results when using an angle from the range of 130° to 170°, especially from 148° to 163°. The angle α should advantageously be greater than or equal to 7°. In the sample embodiment, it is 9°. In other embodiments, it can also be chosen from a range of 7° to 40°.

[0077] In the sample embodiment of the present disclosure discussed here, it is not absolutely necessary, if the wedge effect is strong enough, to maintain the position of the cam in its clamping position by outside measures. This already occurs simply due to the fact that the gear 107 can only turn in one rotary direction and this is in fact blocked in removable fashion by the clamp 33. In sample embodiments of the present disclosure, the camlike clamping element is held in position by the spring force of a spring element 159. For this, the spring element 159 lies against the clamping element above the shifting axis 143 and turns or holds the clamping element 29 in its clamping position. In order to remove the clamping element from its clamping position, the spring force must be overcome with a switch 160. Using the switch 160, both clamps 29 and 33 can be activated at the same time. Depending on the arrangement of the switch/button, a pulling or pressing of the switch can overcome the spring force and release the ring gear 107 from the clamp 33 and lock the planet carrier 105. In the other movement of the switch/button, the clamp 29 and the planet carrier 105 are again released via the spring force, while the clamp 33 locks the ring gear 107.

TABLE-US-00001 List of reference symbols  1 strapping device  2 housing  3 handle  4 base plate  6 tensioning apparatus  6a tensioning axis  7 tensioning wheel  8 rocker  8a rocker pivot axis  9 tensioning plate  10 button  12 friction welding mechanism  13 welding shoe  14 transmitting mechanism  15 storage battery  19 bevel gear  20 bevel gear  21 gear  22 toothed belt drive  23 gear  24 shaft  25 planet carrier  25a clamping surface  25b planet gears  26 gearing  27 ring gear  27a shoulder  27c cam  28 roller bearing  29 first clamp  29a arc-shaped contact surface  30 sun gear  31 axis of rotation of gearing and tensioning wheel  32 ring gear  32a outer surface  33 second clamp  34 planet gear  35 planet carrier  36 sun gear  37 planet carrier  37a shoulder  38 planet gear  39 stop element  40 arrow  41 planet gear  42 planet carrier  43 sun gear  44 spring element (restoring spring)  45 freewheeling  46 abutment  46a recess  80 pivoting rocker  80a rocker pivot axis  80b dog  80c dog  86 tensioning apparatus  86a tensioning axis  87 tensioning wheel  89 tensioning plate  99 bevel gear 100 bevel gear 105 spur gear (planet carrier) 105b planet gear 106 gearing 107 ring gear 107b circumferential surface 109 ring gear 109b circumferential surface 109c external toothing 110 sun gear 112 arrow 113 arrow 114 planet gears 115 planet carrier 117 planet carrier 117b toothing 117a cam 117b cam 117c toothing 118 planet gear 121 planet gear 122 planet carrier 123 sun gear 124 spring element 125 freewheeling 143 shifting axis 150 circular arc segment 150c toothing 151 connection shaft 151a connection axis 155 distance/swivel radius 156 connection line 157 rotary direction 158 radius 159 spring element 160 switch B strap M motor