EP2897866B1 - Umreifungsvorrichtung mit einer schwenkbaren wippe - Google Patents

Umreifungsvorrichtung mit einer schwenkbaren wippe Download PDF

Info

Publication number
EP2897866B1
EP2897866B1 EP13805503.3A EP13805503A EP2897866B1 EP 2897866 B1 EP2897866 B1 EP 2897866B1 EP 13805503 A EP13805503 A EP 13805503A EP 2897866 B1 EP2897866 B1 EP 2897866B1
Authority
EP
European Patent Office
Prior art keywords
tensioning
wheel
strap
rocker
strapping device
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP13805503.3A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP2897866A1 (de
Inventor
Favio FINZO
Mirco Neeser
Dimitrios Takidis
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Signode International IP Holdings LLC
Original Assignee
Signode International IP Holdings LLC
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=49765564&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP2897866(B1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Signode International IP Holdings LLC filed Critical Signode International IP Holdings LLC
Publication of EP2897866A1 publication Critical patent/EP2897866A1/de
Application granted granted Critical
Publication of EP2897866B1 publication Critical patent/EP2897866B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • 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
    • 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
    • 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
    • B65B13/025—Hand-held tools
    • 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
    • B65B13/185—Details of tools
    • 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
    • B65B13/185—Details of tools
    • B65B13/187—Motor means
    • 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
    • B65B13/24—Securing ends of binding material
    • B65B13/32—Securing ends of binding material by welding, soldering, or heat-sealing; by applying adhesive
    • 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
    • B65B13/24—Securing ends of binding material
    • B65B13/32—Securing ends of binding material by welding, soldering, or heat-sealing; by applying adhesive
    • B65B13/322—Friction welding

Definitions

  • the invention relates to a strapping device for strapping packaged goods with a strapping tape, which has a tensioning device for applying a tape tension to a loop of a strapping tape, the tensioning device being provided with a motor-driven tensioning wheel that can be rotated around a tensioning axis and is provided for engaging the strapping tape , the tensioning device further comprises a tensioning plate, with provision being made during a tensioning process carried out by the tensioning device that a single or multi-layer section of the strap is located between the tensioning wheel and the tensioning plate and is in contact with both the tensioning wheel and the tensioning plate, furthermore the clamping plate is arranged on a rocker pivotable by motor about a rocker axis in order to either increase or decrease a distance between the clamping wheel and the clamping plate by a pivoting movement of the rocker, as well as a connecting device for generating a d extraordinary connection, in particular a welded connection, at two superimposed areas of the loop of the strapping band by means of a
  • Such strapping devices are used for strapping packaged goods with a plastic strap.
  • a loop of the respective plastic strap is placed around the packaged goods.
  • the plastic tape is pulled off a supply roll.
  • the end area of the tape overlaps with a section of the tape loop.
  • the strapping device is now placed on this two-layer area of the strap, the strap is clamped in the strapping device, strap tension is applied to the strap loop by means of the tensioning device, a closure is created by friction welding on the loop between the loaded strap layers.
  • a friction shoe moving in an oscillating manner is used to press the belt in the area of two ends of the belt loop.
  • the pressure and the heat generated by the movement melts what is usually plastic Tape locally for a short time. This creates a permanent connection between the two layers of tape that can at most be released again with great force. Thereafter or approximately at the same time, the loop is separated from the supply roll. The respective packaged goods are strapped as a result.
  • Strapping devices of the generic type are intended for mobile use, in which the devices should be carried by a user to the respective place of use and there should not be dependent on the use of externally supplied supply energy.
  • the energy required for the intended use of such strapping devices for tensioning a strapping band around any packaged goods and for creating a seal is usually provided by an electric accumulator or by compressed air in previously known strapping devices. This energy is used to generate the strap tension applied to the strap by means of the tensioning device and a closure on the strapping strap.
  • Strapping devices of the generic type are also intended to connect exclusively weldable plastic straps to one another.
  • a low weight is of particular importance in order to put as little physical strain as possible on the users of the strapping device when using the device.
  • the weight should be distributed as evenly as possible over the entire strapping device, in particular in order to avoid concentration of the weight in the head area of the strapping device. Such a concentration leads to unfavorable handling properties of the device.
  • the most ergonomic and user-friendly handling of the strapping device is always aimed for. In particular, the possibility of operating errors and malfunctions should be as low as possible.
  • slippage can prevent the belt tension values to be achieved from being reached.
  • slippage can also lead to the tensioning process and thus the entire strapping process extended in time.
  • slippage also means that the number of straps that can be achieved with one charge of the accumulator is reduced.
  • slip also means that the belt tension value to be achieved may not be achieved and the belt is therefore not sufficiently tensioned, which can represent a safety risk.
  • the tensioning wheel is usually provided with teeth and is pressed onto the tensioning plate with a pressure force.
  • the pressing force can result from a spring with which the rocker with the tensioning wheel arranged on it presses against the band and the tensioning plate arranged below.
  • these solutions are not particularly satisfactory when higher belt tensions are to be generated, since - as has been shown - this does not allow slip during the tensioning process to be prevented with sufficient certainty.
  • a rocker arm assembly of a strapping machine comprising: a rocker arm comprising: a fulcrum end, a swing end, and a seat formed on the rocker arm located adjacent to the swing end.
  • the invention is therefore based on the object of creating a generic, in particular a mobile, strapping device of the type mentioned at the beginning with high functional reliability, in which the intended strap tensions can be applied to the strap safely and with as little slip as possible.
  • a drive movement is carried out by means of a transmission means of the strapping device during the duration of the tensioning process swiveling rocker is transmitted, the Drive movement is provided for exerting a torque on the rocker.
  • the torque exerted on the rocker can be used to increase the pressing force of the tensioning device against the strapping band.
  • the torque exerted on the rocker by transmission means can originate from a motor, the drive torque of which increases the pressing force of the rocker against the band in the course of the tensioning process.
  • the motor-related increase takes place in such a way that it occurs primarily during or after an increase in the belt tension. It is advantageous here if a motor is used to generate the motor torque for the rocker, which also performs other drive movements. It is particularly favorable here if the motor and its drive movement are used, with which the tensioning wheel is also driven. On the one hand, a further motor can thereby be avoided, but the function according to the invention can still be exercised. On the other hand, the motor torque, which usually rises when the belt tension increases, can also be used to increase the pressing force. In a structurally particularly simple manner, this allows the rocker to be pressed against the band in a variable, voltage-dependent manner. The latter can preferably take place proportionally to the respectively applied belt tension.
  • a torque is exerted and transmitted on the rocker that is based on a force exerted on the tensioning device by the band at an engagement point of the band with the tensioning device.
  • This force the reaction of the tensioning force applied to the belt by the driven tensioning wheel, is picked up at a suitable point and transmitted to the rocker with a transmission device.
  • the belt tensioning force acting on the tensioning wheel is used on the tensioning wheel itself. This uses the momentary torque acting on the tensioning wheel, which is introduced from the tensioning wheel into the transmission means of the tensioning device and is transmitted by these to the rocker.
  • the motorized drive movement for the tensioning device is also used, at least indirectly as a reaction, to use the rotational movement of the tensioning wheel driven by the motor and a pivoting movement of the rocker during the tensioning process, one of the with the strapping engaged standing tensioning wheel derived torque by means of transmission means in the Rocker can be introduced in order to increase a pressing force of the tensioning device against the band.
  • a transmission of the tensioning device with which a motorized drive movement for the tensioning wheel is reduced or translated, can be wholly or partially part of the transmission means with which the force acting on the tensioning wheel and resulting from the belt tension from the belt the rocker is transferred.
  • means are provided for the band tension-dependent variable pressing of the tensioning wheel onto the strapping band.
  • the tensioning device is pressed against the strapping in a variable manner depending on the tension of the tape.
  • the belt tension generated by the tensioning process is thus used to advantageously increase the pressure of the tensioning wheel on the belt with steadily increasing belt tension . Slippage of the tensioning wheel during the tensioning process can be counteracted. With increasing belt tension, the contact pressure of the tensioning wheel on the belt and the tensioning plate also increases.
  • the invention enables a high pressure to be exerted on the belt when the belt tension is already high and the risk of slippage between the tensioning wheel and the belt is also particularly high when attempting to further increase the belt tension.
  • the pressure force which preferably increases automatically, i.e. without manual intervention, can counteract the increasing risk of slippage and thus ensure functional reliability and a fast strapping process even with high strap tensions. Since the reaction of the strapping tape to the action, namely the applied tape tension, as well as transmission means are used which are derived from the tensioning device, in particular from the tensioning wheel, and transmitted to the rocker, no intervention by an operator is required to achieve the effect according to the invention, the effect according to the invention is advantageously achieved automatically in the strapping device.
  • the transmission means which advantageously represent an operative connection from the tensioning wheel to the rocker, can comprise a pivotable mounting of the rocker at least during the tensioning process and a rotatably or rotatably mounted gear element which is operatively connected to the tensioning wheel during the tensioning process .
  • the reaction force of the band is preferably used as torque and is introduced into the rotatable or rotatable gear element, for example a planet carrier of a planetary gear.
  • the rotatable or rotatable gear element should be supported against the rotary or rotational movement on a support element.
  • the reaction force of the tensioning wheel can then be introduced into the rocker via or due to the support, whereby an additional torque acts on the rocker, which can be used to increase the pressing force of the rocker against the strapping.
  • the transmission means can advantageously be wholly or partially a component of the tensioning gear, with which a motorized drive movement or a drive movement originating from some other energy supply is directed to the tensioning wheel at a suitable speed.
  • motorized drive movements with identical directions of rotation of only one motor can be used not only for driving the tensioning wheel when tensioning the strapping but also for lifting the rocker.
  • the belt tension-dependent variable pressing of the tensioning wheel onto the belt to be tensioned can also be carried out with the same drive movement. The dependency is provided in such a way that as the belt tension increases, the contact pressure exerted on the belt by the tensioning wheel also increases. Since the risk of slippage between the tensioning wheel and the belt increases with increasing belt tension, the risk of slippage can be counteracted by increasing the contact pressure.
  • the motor drive movement when tensioning the strap can preferably be used in such a way that, during the tensioning process of the strapping tape, one of the strapping bands is transferred to the tensioning wheel by means of the tensioning wheel engaging the strapping tape and rotating against a strap tension acting counterforce is used to increase the contact pressure of the tensioning wheel tensioning wheel in the direction of the clamping plate.
  • a force resulting from the belt tension and acting in a gear mechanism, with which a drive movement is transmitted to the tensioning wheel is to be made possible with little structural effort and ease of use.
  • a solution for this further aspect of the invention, which can be significant in combination with the subject matter of claim 1, is described in claim 8. This thus relates to a locking device for use in a strapping device, with which a rotatable wheel can be clamped which is provided for transmitting a drive movement, in particular a gear wheel of a tensioning device of the strapping device.
  • the locking device should have at least one clamping body which can be pivoted about a pivot axis and is arranged at a distance from the wheel, which can be pivoted from a release position to a locking position in which it - preferably with part of an arcuate contact surface - abuts against a substantially flat, i.e. free of form-locking element , Circumferential clamping surface of the wheel arrives, wherein the clamping body has a pivot radius which is greater than a distance between the pivot axis of the clamping body and the peripheral clamping surface of the wheel, and the direction of rotation of the clamping body around the pivot axis when moving from the release position to a clamping position in opposite directions of rotation such as the wheel to be clamped runs.
  • locking of rotating gear wheels can be achieved in a structurally simple manner and in a very functionally reliable manner.
  • the locking in the direction of rotation of the wheel can be maintained with little effort.
  • the clamping force of the clamping body even increases automatically if an attempt is made to turn the wheel further by increasing the torque.
  • the locking device can be used to advantage, in particular, for releasably locking a wheel of a gear that belongs to a gear with which a drive movement is to be transmitted to a tensioning wheel of the tensioning device of a strapping device.
  • it can be provided in particular to clamp a wheel of a planetary gear, with which the drive movement is to be transmitted to the tensioning wheel.
  • one of at least two output directions of the transmission can preferably be determined, in particular an output direction of the transmission on the tensioning wheel, so that the belt can be tensioned,
  • the belt tension acting on the tensioning wheel and the gear is at least partially, preferably completely, relieved. Since with such locking devices comparatively low release forces are required to release the clamping even at high strap tension values, the invention results in particularly functionally reliable and easy-to-use strapping devices.
  • the low operating or actuation forces also make it possible to dispense with a rocker lever, with which high torques were previously generated in previously known strapping devices for lifting the rocker from the tensioned strap. Instead of a long rocker lever, a button or button can now be used, with which the tension-releasing process takes place.
  • the exclusively hand-operated strapping device 1 shown has a housing 2 which surrounds the mechanism of the strapping device and on which a handle 3 for handling the device is formed.
  • the strapping device is also provided with a base plate 4, the underside of which is provided for arrangement on an object to be packaged. All functional units of the strapping device 1 are fastened on the base plate 4 and on the carrier of the strapping device (not shown in detail) which is connected to the base plate.
  • a plastic tape B for example made of polypropylene (PP) or polyester (PET), which was previously placed around the object to be packaged, can be tensioned by means of a tensioning device 6 of the strapping device.
  • the tensioning device has a tensioning wheel 7 with which the band B can be gripped for a tensioning process.
  • the tensioning wheel 7 is arranged on a pivotable rocker 8 which can be pivoted about a rocker pivot axis 8a.
  • the tensioning wheel 7 can be removed from the tensioning plate 9 and pivoted back into its starting position, whereby the tape located between the tensioning wheel 7 and the tensioning plate 9 is released for removal.
  • the two layers can then be welded in a manner known per se by means of the friction welding device 12 of the strapping device at a point on the tape loop at which two layers of the tape lie one above the other. This allows the tape loop to be closed permanently.
  • the friction welding and cutting device 12 is driven by the same only one motor M of the strapping device, with which all other motor-driven movements are also carried out.
  • a freewheel not shown in detail, which causes the drive movement in the respective drive direction of rotation to the corresponding functional unit of the Strapping device is transmitted and no transmission takes place in the respective other drive direction of rotation of the motor provided for this purpose.
  • the friction welding device 12 is provided with a welding shoe 13, shown only in a highly schematic manner, which is transferred by means of a transfer device 14 from a rest position at a distance from the band to a welding position in which the welding shoe is pressed against the band.
  • the welding shoe that is pressed onto the strapping band by mechanical pressure and the simultaneous oscillating movement of the welding shoe at a predetermined frequency melts the two layers of the strapping band.
  • the locally plasticized or melted areas of the band B flow into one another and after the band B has cooled down, a connection is created between the two band layers. If necessary, the band loop can then be separated from a supply roll of the band by means of a cutting device, not shown in detail, of the strapping device 1.
  • the infeed of the tensioning wheel 7 in the direction of the tensioning plate 9, the rotary drive of the tensioning wheel 7 around the tensioning axis 6a, the lifting of the tensioning wheel from the tensioning plate, the infeed of the friction welding device 12 by means of the transfer device 14 of the friction welding device 12 as well as the use of the friction welding device 12 per se and the actuation of the cutting device are carried out using only one common electric motor M, the provides a drive movement for each of these components of the strapping device.
  • an exchangeable and, in particular, removable accumulator 15 which is used to store electrical energy, is arranged on the strapping tool.
  • the supply of other external auxiliary energy, such as compressed air or other electricity, can be provided, but is carried out in the strapping device according to FIGS Fig. 1 and 2 Not.
  • Fig. 4 it is provided in the strapping device to tap its drive movement either for the tensioning device 6 or for the friction welding device 12 at two points on the drive shaft of the motor M.
  • the motor M can be operated in either of the two directions of rotation.
  • the transfer of the drive movement to the clamping device 6 or to the friction welding device 12 is changed automatically by a freewheel arranged on the drive shaft of the motor M (and not shown in detail) depending on the direction of rotation of the drive shaft of the motor.
  • the drive movement is transmitted to the clamping device 6 in one direction of rotation of the drive shaft. Because of the freewheeling mechanism, the friction welding device 12 does not experience any drive movement. In the other direction of rotation, the clamping device 6 is without drive movement and the friction welding device 12 is driven. Any manual switching operations are not required to change the direction of transmission of the motorized drive movement.
  • Such freewheels are already known in connection with strapping devices, which is why they will not be discussed in more detail.
  • the motorized transmission of the drive movement to the friction welding device 12 and transfer device 14 takes place by suitable means.
  • This can be, for example, a toothed belt drive with an annularly closed toothed belt that is guided over two toothed wheels.
  • One of the two gears is arranged on the drive shaft of the electric motor M, the other belongs to a transmission of the friction welding device 12, with which the motorized drive movement of both the transfer device 14 and the welding shoe 13 of the Reibschwelss adopted 12 moved.
  • the welding shoe which is pressed onto two superimposed layers of the strapping band, can thereby be set in an oscillating movement with a predetermined frequency and amplitude, with which the two band layers are locally melted in the area of the welding shoe and then welded to one another through the subsequent cooling.
  • a bevel gear 19 On the drive shaft of the motor, seen from the motor M, behind the toothed belt drive to the welding device, there is a bevel gear 19, which also belongs to a bevel gear of the clamping device, as does a second bevel gear 20 with which it meshes.
  • a first gear 21 of a further toothed belt drive 22 On the same shaft on which the second bevel gear 20 is arranged there is also a first gear 21 of a further toothed belt drive 22, which is also guided via a second gear 23.
  • the first gear 21 of the toothed belt drive 22 is arranged on the shaft 24 in a rotationally fixed manner.
  • the rocker 8 of the strapping device is pushed onto the other end of the shaft 24 and is part of the tensioning device 6 and carries the tensioning wheel 7 as well as a gear upstream of the tensioning wheel 7, here a planetary gear 26, for which purpose suitable bearings can be provided on the rocker 8 .
  • the rocker 8 is pushed onto the shaft 24 in such a way that it is arranged and supported so that it 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 be pivoted.
  • the planetary gear 26 can be designed as a single or multi-stage planetary gear, in particular as a two- or three-stage planetary gear.
  • An input-side externally toothed sun gear 30 belonging to the planetary gear 26 projects from an end face of the gear wheel 23 facing the tensioning wheel 7, the axis of rotation of which is identical to the axis of rotation 6a of the input-side gear wheel 23.
  • the sun gear 30 is passed through a ring gear 27 and through a central recess of a planet carrier 25, which are also part of the planetary gear 26.
  • the planet carrier 25 Seen from the input side of the planetary gear, the planet carrier 25 is on the axis of the planetary gear 26, the corresponding to the clamping axis 6a, arranged behind the ring gear 27.
  • the planet carrier could also be designed in such a way that it represents a clamping, coupling or spur gear.
  • the ring gear 27 has on its outer circumference a cam 27c which is in engagement with a support 46 fastened to the base plate 4 of the strapping device.
  • the internally toothed ring gear 27 is supported here in such a way that the cam 27c can execute slight relative movements within its engagement in the support 46, for example in a recess 46a of the support.
  • the ring gear 27 also has an annular shoulder 27a on which a roller bearing 28 for supporting the planetary gear 26 is arranged.
  • the planetary carrier 25 the axis of which is aligned with the clamping axis 6a, is in engagement with its three planetary gears 25b with an internal toothing of the input-side ring gear 27 of the planetary gear 26.
  • the planetary gears 25b of the planetary carrier 25 are also in engagement with the sun gear 30, of which one Record drive movement and can transmit to the ring gear 27 and correspondingly reduced. With a rotationally fixed arrangement of the planetary carrier 25, a rotational movement of the sun gear 30 can thus be converted into a rotational movement of the ring gear 27.
  • a first clamp 29 of a locking device is designed as a pivotable 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 it at a distance.
  • the cam is arranged in such a way that when the cam comes into contact with the clamping surface 25a, the clamping effect is further intensified by a rotation of the planetary carrier 25 on the input side in the direction of rotation provided for the planetary carrier 25.
  • the cam onto the clamping surface 25a on the basis of a corresponding switching process, the planet carrier 25 can be blocked against rotation.
  • the cam 29 can be removed from the clamping surface 25a and the planet carrier 25 can thus be released for rotational movements.
  • the switching process can trigger a pivoting movement of the terminal 29 about a switching axis 143, which is triggered by pressing a button 44.
  • the sun gear 30 is also arranged in the area of the axis of rotation 31 of a ring gear 32, the non-toothed outer surface 32a of which is assigned to a second clamp 33.
  • the axis of rotation 31 is identical to or is aligned with the clamping axis 6a.
  • the clamp 33 interacting with the outer surface 32a can in principle be designed in the same way as the first clamp 29 as a switchable cam that can be moved between two end positions, the ring gear 32 being blocked against rotation in one position and for rotational movements in the other position is released.
  • an internal toothing of the ring gear 32 is in engagement with three planet gears 34, which are mounted on the end face of the following planet carrier 35 facing the ring gear 32.
  • the planet gears 34 of the planet carrier 35 are also in engagement with the sun gear 30 of the input-side gear 23, which protrudes into the ring gear 32.
  • the locking device is designed in such a way that one and only one of the wheels 25, 32 is always clamped against rotation and the other wheel 25, 32 is free for rotational movements of the gear 23 and the sun gear 30 either leads to a rotation of the planet carrier 35 about the clamping axis 6a and rotation axis 31 due to a movement of the planet gears 34 in the internal toothing of the ring gear 32. Or the rotation of the sun gear 30 leads, depending on the positions of the locking device, to a rotation of the ring gear 32. If the planet carrier 25 is not clamped by the locking device, the rotating sun gear takes the planet gears 25b with it in such a way that the planet carrier 25 rotates and the ring gear 27 remains stationary.
  • the ring gear 32 If, on the other hand, the ring gear 32 is not clamped, a rotation of the sun gear 30 leads to 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 gear 26 towards the tensioning wheel 7 is greater than the torque to be overcome in order to set the ring gear 32 in rotation, the ring gear 32 in particular rotates and the tensioning wheel 7 rotates at least substantially Not.
  • a further sun wheel 36 which has planetary gears, is non-rotatably arranged on the latter 41 of another planet carrier 42 meshes.
  • a further sun gear 43 directed towards the tensioning wheel 7 and connected in a rotationally fixed manner to the planet carrier 42 is passed through a recess in the further planet carrier 37, which is designed as a ring gear.
  • the sun gear 43 is in meshing engagement with the planet gears 38 of the further planet carrier 37 facing the tensioning wheel 7.
  • the planet gears 38 of the second planet carrier 37 again mesh with an internal toothing of the tensioning wheel 7 and drive the latter to rotate about the tensioning axis 6a.
  • the third planet carrier 37 has on its outer surface a shoulder 37a which can be brought into contact against a stop element 39 by a rotational movement.
  • the stop element 39 itself is not fixed on the rocker but on the base plate 4 or some other carrier which does not take part in the pivoting movement of the rocker 8. The stop element 39 is thus stationary with respect to the shoulder 37a.
  • the strapping device 1 behaves as follows: After a tape loop with a commercially available plastic strapping tape has been placed around the respective packaged goods, this is inserted into the strap strapping device in the area of the strap end, in which the strap loop is partially double-layered, and the The end of the strap is held in place in the strapping tool with a strap clamp (not shown). A section of the tape B directly adjoining the tape loop is placed in two layers over the tensioning plate 9 of the tensioning device 6.
  • the rocker 8 with the tensioning wheel 7 and the upstream gear 26 is here in its upper end position, in which the tensioning wheel 7 is arranged at a distance (with its greatest intended distance) from the clamping plate 9, which results in the largest possible opening gap, which is a allows easy, comfortable and thus also quick insertion of the tape into the tensioning device.
  • the rocker is then lowered onto a tensioning plate 9 opposite the tensioning wheel 7 and pressed against the band arranged between the tensioning plate 9 and the tensioning wheel 7.
  • Transfer movement of the tensioning wheel as well as the level of the contact pressure exerted by the tensioning wheel on the belt at the beginning of the tensioning process can be generated by one or more pretensioned spring elements 44 (not shown).
  • the spring element By pressing a button 10, the spring element can be released and the entire strapping process with its successively executed process sections “tensioning”, “locking production”, “cutting”, releasing the tension from the strap in the area of the tensioning device, and "lifting the rocker” can be triggered, including no further intervention by the operator of the strapping tool has to be carried out.
  • the motorized drive movement is transmitted to the tensioning wheel 7.
  • the second clamp 33 is now moved into its position in which it presses against the ring gear 32.
  • the ring gear 32 is hereby arrested and locked against rotational movements.
  • the first terminal 29, however, is still positioned at a distance from the planet carrier 25 on the input side and releases the ring gear 27 for rotational movements.
  • the motor drive movement which, due to the intended specific direction of rotation of the motor M, is transmitted via the bevel gear 19, 20, 21 to the second toothed belt drive 22 and thus to the gear 23, arrives from here in the sequence of the gear members mentioned below via the input-side 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 on the tensioning wheel 7 Required with a correspondingly high torque - be driven in the predetermined direction of rotation.
  • This counterforce acts in the opposite direction of transmission as the motorized drive movement, on all of the Transmission of the drive movement involved gear members of the multi-stage planetary gear. If another type of gear than a single or multi-stage planetary gear is used, the counterforce resulting from the already applied belt tension and introduced into the respective gear via the contact with the tensioning wheel is available for use. This counterforce can be used to improve the process conditions, in particular the functional reliability, even when the belt tensions to be applied are high. In order to use this counterforce for the purpose described below, it would in principle be possible to use each of these gear members for this purpose, in particular to pick up and use the said counterforce on each of these gear members.
  • the planet carrier 37 is used for this.
  • the planet carrier 37 is supported on the base plate 4 via the stop element 39, whereby the entire tensioning device 6 is pressed onto the belt around the rocker axis 8a in proportion to the resistance force (belt tension).
  • the tensioning wheel 7 is thus pressed onto the belt B in proportion to the belt tension.
  • the belt tension generated by the tensioning process is used to advantageously increase the pressing force of the tensioning wheel 7 on the belt B as the belt tension increases, which increases the risk of the tensioning wheel "slipping through” or slipping as the belt tension increases 7 can be counteracted during the tensioning process.
  • the planet carrier is formed with the engagement element 37a, which interacts with the stationary stop element 39.
  • the engagement element which is designed as a cam and is arranged on the outer circumference of the planet carrier and protruding essentially radially from the latter, is supported on the stop element 39.
  • the stationary stop element 39 is for this purpose in the area of the head end of the strapping device.
  • the stop element 39 is located on one side, namely the head end, the clamping axis 6a and the rocker pivot axis 8a running essentially parallel to it on the other side of the clamping axis 6a.
  • the rocker 8, on which the planet carrier 37 is arranged to be rotatable about the clamping axis 6a via a roller bearing, is also at least during the clamping process pivotable, ie not blocked against pivoting movements but released for this.
  • the planet carrier 37 can be rotated about the clamping axis 6a during the clamping process.
  • the belt tension generated in response to the tensioning process in belt B causes a force on the tensioning wheel 7 that is opposite to the direction of rotation of the tensioning wheel provided during the tensioning process that the planet carrier 37 is pressed with increased force against the belt in the direction of the clamping plate 9.
  • This resulting torque is in turn proportional to the resulting pressing force acting on the belt B by the tensioning wheel 7, with which the belt B is pressed by the tensioning wheel 7 against the tensioning plate 9.
  • a belt tension increasing from the motorized drive movement on the tensioning wheel 7 is therefore accompanied by an increasing pressing force of the tensioning device on the belt.
  • the tape should be able to be removed quickly and without complications from the strapping device.
  • a motorized lifting movement of the tensioning wheel 7 out of the tensioning position is provided.
  • the button is actuated and as long as the button 10 is actuated, the rocker also remains in the open position, in which a sufficient distance between the clamping plate 9 and the tensioning wheel 7 is created. Releasing button 10 closes the rocker, for example by spring force.
  • the operative connection between the electric motor M and the cutting wheel 7 is first released and an operative connection between the electric motor M and the rocker 8 is created.
  • This is achieved by switching terminals 29, 33.
  • the previously existing clamping of the ring gear 32 is canceled in that the second clamp 33 is removed from the outer surface 32a of the ring gear 32 is removed and this thereby releases the ring gear 32 for rotational movements.
  • the first clamp 29 is lowered onto the clamping surface 25a of the planet carrier 25 and brought into clamping contact therewith.
  • the planetary carrier 25 on the input side is fixed and locked against a rotational movement about the clamping axis 6a, along which the entire planetary gear is located.
  • the tensioning wheel 7 can rotate freely in a drive-free manner and no longer has an operative connection to the electric motor M and to the sun wheel 30, which could transmit a drive movement.
  • a drive movement of the electric motor M with the same direction of rotation as during the tensioning process is now used due to the blocking of the input-side planetary carrier 25 of the planetary gear so that the planetary gears 25b of the spur gear 25 drive the input-side ring gear 27 with them during their rotational movement.
  • the input-side ring gear 27 thus executes a rotational movement due to the rotating planet gears 25b.
  • the contact and support of the ring gear 27 on the support element 46 leads to a pivoting movement of the ring gear 27 about the rocker axis 8a.
  • the strapping device is now ready for a subsequent new strapping, which can be done in the same way as the strapping described above.
  • the spring element 44 For the subsequent lowering of the rocker 8 after the introduction of a new section of the strapping band B into the strapping device 1, the spring element 44 must be released again, which can be done, for example, via an operable button on the strapping device. It will do this the one before pressed button 10 released.
  • the spring force then pivots the rocker 8 in the reverse pivoting direction towards the tensioning plate and clamps the band with an initial pressure force between the tensioning wheel 7 and the tensioning plate 9 for the subsequent tensioning process.
  • the pressure force which is variable in the further course of the clamping process, increases as described.
  • FIG. 5 to 9 An exemplary embodiment of a strapping device according to the invention is shown. In terms of its external appearance, this can also be the representation of Fig. 1 are equivalent to.
  • the basic structure of this embodiment of the strapping device can also correspond to that of the example discussed above. Accordingly, only one motor M is used in this embodiment as well, which has the in Fig. 5 Not shown welding device 12 and separating device is provided on the one hand in one of the two directions of engine rotation and the clamping device 6 on the other hand in the other direction of engine rotation.
  • the optional drive of either the welding device and cutting device on the one hand or the clamping device 6 on the other hand takes place via a freewheel and different directions of rotation of the motor M.
  • the embodiment also has a pivotable rocker 80 of the clamping device 86 that is motor-driven about a rocker pivot axis 80a.
  • a pivotable rocker 80 of the clamping device 86 that is motor-driven about a rocker pivot axis 80a.
  • it is not the tensioning wheel 87 but the tensioning plate 89 that is arranged on the pivotable rocker 80, the rocker pivot axis 80a of which runs parallel to the tensioning axis 86a.
  • the motorized drive movement with the direction of rotation which is used for rotational movements about the clamping axis 86a, is also used in this exemplary embodiment for the pivoting movement of the rocker 80.
  • the rocker pivot axis 80a runs essentially parallel to the tensioning axis 86a, about which the tensioning wheel is rotatably mounted.
  • the rotational movement of the motor is transmitted via a bevel gear pair 99, 100 to a planetary gear 106 and passed on from there to the tensioning wheel 87.
  • a freewheel 125 arranged on the shaft of an input-side sun gear 110 it is ensured that the input side of the Planetary gear 106 can only rotate in one direction of rotation.
  • the planetary gear 106 is provided with gear elements which, as in the example described above, can be optionally locked by means of a locking device comprising two clamps 29, 33, whereby the drive movement can be transmitted either to the tensioning wheel 87 or to the rocker 80.
  • the ring gear 107 is released via the locking device, ie the clamp 33 is not in clamping engagement with the ring gear 107.
  • the tensioning wheel 87 can thereby rotate freely without an operative connection with the motor M. Any tape tension retroactive from the just preceding tensioning operation from the strapping B onto the tensioning wheel 87 is thereby released by the tensioning wheel 87 and the gear unit 106 connected upstream of the tensioning wheel.
  • the spur gear which is designed as a planetary carrier 105 and whose axis of rotation is aligned with the clamping axis 86a, that is to say the axis of rotation of the tensioning wheel 87, is blocked with the clamp 29.
  • the motor drive movement transmitted from the bevel gear 100 to the input-side sun gear 110 cannot lead to a rotation of the planet carrier 105 but to rotational movements of the planet gears 105b of the planet carrier 105 due to the releasable rotational locking of the planet carrier 105 made by means of the clamp 29.
  • the internal toothing of the ring gear 109 which meshes with these planetary gears 105b, sets the latter in rotation.
  • an external toothing 109c of the ring gear 109 is in engagement with an external toothing 150c of a circular arc segment 150 which is arranged in a stationary manner on one end of a connecting shaft 151.
  • the connecting axis 151a of the connecting shaft 151 runs parallel to the stationary clamping axis 86a of this exemplary embodiment.
  • the ring gear 109 could also be supported on a support element via a cam, in which case either the cam or the support element should neither be attached to the ring gear 109 nor designed to be movable and the other of the two elements should be arranged on the ring gear 109.
  • the connecting axis 151a is on one and the rocker pivot axis 80a on the other side of the tensioning axis 86a, the rocker pivot axis 80a being on the side of the head-side end of the strapping device.
  • the planet carrier 117 belongs to the drive train which is provided for the drive movement of the tensioning wheel 87.
  • the operative connection of this drive train to the motor M is momentarily interrupted due to the switching position of the locking device described above.
  • the planet carrier 117 rotates about the clamping axis 86a and takes along a driver 80c of the rocker 80 with a cam 117a arranged on its outer circumferential surface.
  • the rocker 80 which is arcuate in relation to a plan view, rotates as a result and is opened.
  • the rocker 80 which is rotatably mounted about the rocker axis 80a and has approximately the shape of a curved section, is arranged with its lower free end below the tensioning wheel 87, so that the tensioning plate 89 arranged in the area of the free end of the rocker 80 are also arranged directly below the tensioning wheel 87 can.
  • the clamping plate 89 In order to arrange the clamping plate 89 at a distance from the tensioning wheel 87, the previously described motor-driven movement of the rocker 80 in the direction of rotation according to arrow 112 ( Fig. 6 ), by means of which the rocker 80 is opened as described and a distance between the tensioning wheel 87 and the tensioning plate 89 is increased.
  • the opening movement can be limited by a stop.
  • the motor-driven rocker 80 now allows the tensioned and closed strapping loop to be removed from the strapping device. After the finished strapping has been removed, the end of a new strapping loop can be inserted between the tensioning plate and the tensioning wheel for a subsequent tensioning process. Due to the restoring force of the spring element 124 which was previously tensioned during the opening movement, the rocker 80 can be attached to the The tensioning wheel is brought up and the belt is pressed against the tensioning wheel with the initial pressure required for the tensioning process.
  • actuation of a button or other actuating element can be provided, by which the spring force is released to act on the rocker. It can also be a question of releasing the button 10.
  • the ring gear 107 is clamped on its outer circumferential surface by means of the clamp 33 to prevent rotational movements.
  • the planet carrier 105 is not clamped and can therefore rotate just like the connecting shaft 8.
  • the motorized drive movement from the sun gear 30 to the planetary gear 106 arranged on the clamping axle 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 the latter is set in rotation.
  • the sun gear which cannot be seen, drives the planetary gears 121 of a further downstream stage of the planetary gear 106.
  • the planet carrier 122 of this stage also rotates.
  • the sun gear 123 of the last-mentioned stage is passed through the further planet carrier 117 and drives the planet gears 118 of this further stage, which in turn mesh with an internal toothing of the tensioning wheel 87.
  • the tensioning wheel 87 is thus driven in the tensioning direction via the single or multi-stage planetary gear 106 and the inserted tape B is tensioned.
  • the belt tension creates a drag force acting from the belt B on the rotating tensioning wheel 87 in the form of a restoring torque.
  • Their size is variable and proportional to the size of the applied belt tension. This resistance force acts in opposition to the motor drive torque that is present in the transmission elements involved in the transmission of the drive movement.
  • the planet carrier 117 is supported on the rocker 80 with a cam 117b, which has the function of a stop.
  • the planet carrier 117 which rotates in a suitable direction of rotation due to the motorized drive movement, lies opposite with its cam 117b a driver 80b of the rocker and thereby rotates it in a movement according to arrow 113 ( Fig. 6 ) around the rocker axis 80a against the tensioning wheel. If necessary, a noticeable rotational movement about the rocker axis 80a is not actually carried out, but essentially only increases the torque about the rocker axis 80a. In both cases, however, the pressing force with which the rocker 80 presses the tensioning plate 89 or the belt against the tensioning wheel 87 is increased. This increase is usually not done in a single step.
  • the increase in the pressing force of the rocker against the belt which is ultimately due to the motorized drive movement and the already existing belt tension and which occurs through intervention in the tensioning gear 106, is proportional to the force present in the belt and as a resistance against maintaining and against a further increase in belt tension on the belt Point of engagement in the belt, from the belt on the tensioning plate 89 and on the tensioning wheel 87, a resistance or restoring force takes place. As long as the tensioning process increases the belt tension, the resistance force and thus the resulting pressure force also increase.
  • the end positions of the rocker 80 which are possible due to the pivotability of the rocker for opening and closing on the one hand and to increase the pressing force on the band on the other hand are shown.
  • the clamping plate 89 is in one of the two end positions due to a contact of the cam 117b of the planet carrier 117 with a contour of the driver 80b and a direction of rotation of the planet carrier clockwise (with reference to the illustration of Fig. 8 ) the rocker is rotated counterclockwise around its rocker pivot axis.
  • the driver 80b and the cam 117b act like a lever which causes a counterclockwise torque about the rocker pivot axis 80a.
  • Fig. 9 shows the end position of the open rocker.
  • the planet carrier 117 rotates in comparison to Fig. 8 in the opposite direction of rotation and thereby comes into abutment against the driver 80c of the rocker 80.
  • the driver 80c is located in relation to the rocker pivot axis 80a and the other driver 80b on the other side of the rocker pivot axis 80a.
  • the driver 80b is located above and the driver 80c below the rocker pivot axis 80a.
  • the rocker swivels in the illustration of Fig. 9 clockwise and thereby creates a distance from the tensioning wheel 87.
  • Fig. 12 shows a perspective partial view of the clamping device of the embodiment, in which only one of the two clamps is shown.
  • the clamp 33 is brought into contact with the flat and in cross-section essentially exactly circular circumferential surface 107b of the ring gear 107.
  • Fig. 13 a sectional view through the ring gear 107 and the clamp 33 is shown.
  • the ring gear can either be clamped against rotational movements or released again.
  • Each of the in the strapping devices according to Fig. 5-9 provided clamps can preferably be designed according to the locking device described here, but conventional locking devices are also possible.
  • an at least approximately flat circular or arcuate circumferential surface of the wheel interacts with a pivotable clamping element or clamping body.
  • the peripheral surface 107b of the preferred exemplary embodiment shown, which functions as a clamping surface, does not have any latching elements with which a clamping based on a positive engagement of a clamping element in a latching element or a latching recess is provided.
  • the clamping element 33 is mounted pivotably about the switching and pivot axis 143, the switching axis 143 of the clamping element 33 running parallel to the axis of rotation of the wheel 107 to be clamped.
  • the switching axis 143 runs in the area of one end of the cam-shaped clamping element 33.
  • an arcuate contact surface 33a is provided, which is provided for contact with the clamping surface 107b of the wheel to be clamped.
  • the clamping element 33 is arranged in relation to the wheel 107 to be clamped in such a way that the contact line of the contact surface 33a is at a distance 155 from its pivot axis 143 which is greater than the distance between the pivot axis 143 and the clamping surface 107b.
  • the clamping element 33 pivots from its release position into a clamping position, it already comes into contact with the clamping surface 107b at a point that is in front of a straight line 156 connecting the axis of rotation of the wheel 107 with the pivot axis 143 of the clamping element.
  • the contact line is located in front of the (imaginary) connecting line 156.
  • the rotation of the wheel 107 is braked and can only move slightly further. Due to a further rotation against the increasing clamping effect, the clamping effect further intensifies and thereby increasing wedging of the clamping element 33 against the wheel 107 Connection line 156 and presses against the clamping surface 107b.
  • the wheel 107 is clamped against the cam-shaped clamping element 33. Further movement is no longer possible even with an arbitrarily high torque.
  • Fig. 14 the geometric relationships during clamping are shown.
  • the connecting line between the axis of rotation 86a of the wheel 107 and the pivot axis 143 is denoted by 156.
  • the contact surface (circumference) of the wheel could be smooth or slightly structured.
  • the radius of the wheel at the point of contact with the cam is designated as 158 and the pivot radius of the clamping element 33 at the point of contact is designated 155.
  • the pivot radius 155 at the contact point forms an angle ⁇ with the connecting line 156
  • the radius 158 of the wheel 107 forms an angle ⁇ with the pivot radius 155 (in each case at the contact point).
  • the geometric relationships are designed such that in the clamping position in which the wheel 107 is blocked against rotational movements in the intended direction of rotation, the angle ⁇ is at least approximately 155 °.
  • the angle ⁇ should advantageously be greater than or equal to 7 °. In the exemplary embodiment it is 9 °. In other embodiments, it can also be selected from a range from 7 ° to 40 °.
  • the cam-shaped clamping element is held in position by the spring force of a spring element 159.
  • the spring element 159 rests against the clamping element above the switching axis 143 and rotates 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.
  • both terminals 29 and 33 can be operated at the same time.
  • the spring force can be overcome by pulling or pressing the switch and the ring gear 107 released from the terminal 33 and the planet carrier 105 locked. With the respective other movement of the switch / button, the spring force releases the clamp 29 and the planet carrier 105, while the clamp 33 locks the ring gear 107.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Basic Packing Technique (AREA)
EP13805503.3A 2012-09-24 2013-09-24 Umreifungsvorrichtung mit einer schwenkbaren wippe Active EP2897866B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
CH17232012 2012-09-24
CH17242012 2012-09-24
PCT/IB2013/002116 WO2014167377A1 (de) 2012-09-24 2013-09-24 Umreifungsvorrichtung mit einer schwenkbaren wippe

Publications (2)

Publication Number Publication Date
EP2897866A1 EP2897866A1 (de) 2015-07-29
EP2897866B1 true EP2897866B1 (de) 2021-08-04

Family

ID=49765564

Family Applications (2)

Application Number Title Priority Date Filing Date
EP13821914.2A Active EP2897867B1 (de) 2012-09-24 2013-09-24 Umreifungsvorrichtung
EP13805503.3A Active EP2897866B1 (de) 2012-09-24 2013-09-24 Umreifungsvorrichtung mit einer schwenkbaren wippe

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP13821914.2A Active EP2897867B1 (de) 2012-09-24 2013-09-24 Umreifungsvorrichtung

Country Status (7)

Country Link
US (8) US9932135B2 (ja)
EP (2) EP2897867B1 (ja)
JP (2) JP6329151B2 (ja)
CN (2) CN104870315B (ja)
CH (2) CH707028A2 (ja)
ES (2) ES2895662T3 (ja)
WO (2) WO2014167377A1 (ja)

Families Citing this family (45)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9272799B2 (en) 2011-10-04 2016-03-01 Signode Industrial Group Llc Sealing tool for strap
US9468968B2 (en) * 2012-08-30 2016-10-18 Signode Industrial Group Llc Battery powered tensioning tool for strap
JP6329151B2 (ja) 2012-09-24 2018-05-23 シグノード インターナショナル アイピー ホールディングス エルエルシー バンド掛け装置
CH708294A2 (de) * 2013-05-05 2014-12-15 Orgapack Gmbh Umreifungsvorrichtung.
PL3105126T3 (pl) 2014-02-10 2018-11-30 Orgapack Gmbh Urządzenie napinające dla urządzenia taśmującego
US9988163B2 (en) * 2014-05-28 2018-06-05 Hsiu-Man Yu Chen Fiber strap packing machine
US10577137B2 (en) * 2015-12-09 2020-03-03 Signode Industrial Group Llc Electrically powered combination hand-held notch-type strapping tool
CH712984A2 (de) 2016-09-18 2018-03-29 Signode Ind Group Llc Umreifungsvorrichtung zur Umreifung von Packgut mit einem Umreifungsband.
US11981464B2 (en) 2016-11-06 2024-05-14 Golden Bear LLC Strapping tensioning and sealing tool
US10745158B2 (en) * 2016-11-06 2020-08-18 Golden Bear LLC Strapping tensioning and sealing tool
CN106494661B (zh) * 2016-12-09 2023-03-03 重庆锦沙沣包装有限公司 包装袋整理装置
JP6922221B2 (ja) 2016-12-29 2021-08-18 マックス株式会社 結束機
USD864688S1 (en) 2017-03-28 2019-10-29 Signode Industrial Group Llc Strapping device
CH713645A2 (de) 2017-01-30 2018-09-28 Signode Ind Group Llc Umreifungsvorrichtung mit einem Betätigungselement der Spanneinrichtung.
CH713646A2 (de) 2017-01-30 2018-09-28 Signode Ind Group Llc Umreifungsvorrichtung mit einer Spanneinrichtung.
CN116336176A (zh) * 2017-09-03 2023-06-27 深圳市施威德自动化科技有限公司 一种自动扎带工具的三端输入/输出机构
WO2019165142A1 (en) 2018-02-21 2019-08-29 Golden Bear LLC Strapping tool
CN208397169U (zh) 2018-07-05 2019-01-18 台州市新大陆电子科技有限公司 一种带有定位装置的钢筋捆扎机送丝盘制动机构
ES2910036T3 (es) * 2019-02-15 2022-05-11 Titan Umreifungstechnik Gmbh & Co Kg Dispositivo de fleje
US11174051B2 (en) * 2019-02-15 2021-11-16 Samuel, Son & Co. (Usa) Inc. Hand held strapping tool
US11247792B2 (en) * 2019-02-15 2022-02-15 Samuel, Son & Co. (Usa) Inc. Strapping device
EP3696103A1 (de) * 2019-02-15 2020-08-19 TITAN Umreifungstechnik GmbH & Co.KG Umreifungsvorrichtung für insbesondere stahlbänder
IT201900006286A1 (it) 2019-04-24 2020-10-24 Itatools S R L Reggiatrice
IT201900006288A1 (it) 2019-04-24 2020-10-24 Itatools S R L Reggiatrice
CA192340S (en) * 2019-07-22 2021-12-30 Ergopack Deutschland Gmbh Packaging machine
US11511894B2 (en) 2019-09-26 2022-11-29 Hellermanntyton Corporation Cable tie application tool
CN111017282A (zh) * 2019-12-24 2020-04-17 湖南创航科技有限公司 一种手持打包机的收紧轮机构的升降机构
EP3862511A1 (en) 2020-02-10 2021-08-11 Max Co., Ltd. Binding machine
KR102541276B1 (ko) * 2020-04-09 2023-06-13 타이저우 용파이 팩 이큅먼트 컴퍼니 리미티드 용접 장치
US11560247B2 (en) 2020-05-27 2023-01-24 Golden Bear LLC Strapping tool
US20230150704A1 (en) * 2020-07-13 2023-05-18 Signode Industrial Group Llc Strapping tool
AU2021331964B2 (en) * 2020-08-25 2024-06-13 Zhejiang Weipai Packing Equipment Co.,Ltd. Tensioning mechanism
CN114104372A (zh) * 2020-08-25 2022-03-01 台州市永派包装设备有限公司 拉紧机构
US12085065B2 (en) 2020-10-20 2024-09-10 Golden Bear LLC Pump comprising balls for displacement of fluid
CN112550802B (zh) * 2020-11-05 2022-09-06 北京空间机电研究所 一种降落伞封包装置及方法
WO2022095533A1 (zh) * 2020-11-06 2022-05-12 台州市永派包装设备有限公司 压带机构
ES2967495T3 (es) 2020-11-12 2024-04-30 Itatools S R L Mecanismo de control para máquina de inclinación de máquina flejadora
CN112977924A (zh) * 2021-04-15 2021-06-18 安徽燊泰智能设备有限公司 自动打包机送线单元的夹紧机构及其送线单元
CN113460354B (zh) * 2021-07-16 2022-11-15 重庆永源包装设备有限公司 一种打包装置
TWI822092B (zh) * 2021-07-23 2023-11-11 美商賽諾得工業集團有限責任公司 捆紮工具
USD983245S1 (en) * 2021-09-24 2023-04-11 Dongguan Jingduan Packaging Technology Co. Ltd Pallet strapping machine
USD1012641S1 (en) 2021-10-25 2024-01-30 Aptiv Technologies Limited Tool nosepiece
CN114083969B (zh) * 2021-10-29 2024-06-14 如果科技有限公司 双电机驱动桥总成和车辆
CN118742488A (zh) * 2022-02-16 2024-10-01 信诺工业集团有限责任公司 阻力矩被锁定的捆扎工具
WO2024081475A1 (en) * 2022-10-14 2024-04-18 Signode Industrial Group Llc Strapping device with motor-driven rocker

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6109325A (en) * 1999-01-12 2000-08-29 Chang; Jeff Chieh Huang Portable electrical binding apparatus
DE10026200A1 (de) * 2000-05-26 2001-11-29 Cyklop Gmbh Vorrichtung zum Spannen von Umreifungsbändern
WO2009129636A1 (de) * 2008-04-23 2009-10-29 Orgapack Gmbh Umreifungsvorrichtung mit einer spanneinrichtung
DE202011050797U1 (de) * 2011-07-22 2011-11-11 Pantech International Inc. Kipphebelanordnung einer Umreifungsmaschine

Family Cites Families (178)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3028885A (en) * 1958-06-02 1962-04-10 Signode Steel Strapping Co Power strap tensioning tool
US3206167A (en) 1963-11-07 1965-09-14 Stanley Works Strap tensioner device with fulcrum means for pivotal removal of the device
US3284049A (en) 1965-03-31 1966-11-08 Signode Corp Feed wheel drive mechanism for strapping tools
US3367374A (en) 1965-04-08 1968-02-06 Signode Corp Gripper plug
US3360017A (en) 1965-07-16 1967-12-26 Signode Corp Combination strapping tool
US3442733A (en) 1965-08-13 1969-05-06 Signode Corp Combination strap tensioning and sealing tool
FR1513685A (fr) 1966-02-02 1968-02-16 Signode Corp Appareil perfectionné pour cercler des objets au moyen de bandes de cerclage en matière thermoplastique
GB1161827A (en) 1966-11-29 1969-08-20 Naigai Seikosho Kk Band Feeding and Tightening Device of Automatic Strapping Machines.
DE1973947U (de) 1967-09-05 1967-11-30 Banholzer & Wenz Spannvorrichtung fuer bander, insbesondere aus kunststoff, textilien u. dgl.
US3654033A (en) 1970-04-01 1972-04-04 Signode Corp Strap tensioning and sealing tool
US3844317A (en) 1973-06-18 1974-10-29 Signode Corp Strap tensioning tool
US4050372A (en) 1976-01-21 1977-09-27 Signode Corporation Automatic strapping machine
US4011807A (en) 1976-01-21 1977-03-15 Signode Corporation Strap feeding and tensioning machine
US4015643A (en) 1976-01-21 1977-04-05 Signode Corporation Tensioning tool with self-energizing gripper plug
US4020879A (en) 1976-05-28 1977-05-03 Fmc Corporation Power strapping tool
JPS5953143B2 (ja) 1977-06-07 1984-12-24 旭化成株式会社 連続鋳造用鋳型
US4161910A (en) 1978-05-19 1979-07-24 Signode Corporation Strap feeding and tensioning assembly
US4239096A (en) 1978-10-10 1980-12-16 Smilgys Bruno S Power tool safety clutch
GB2041869B (en) 1979-02-23 1982-12-08 Nichiro Kogyo Kk Band feeding and tightening method and device for strapping machinqe
CH637587A5 (de) * 1979-05-11 1983-08-15 Borbe Wanner Ag Vorrichtung zum umreifen von gegenstaenden mit einem kunststoffband.
US4240865A (en) 1979-06-25 1980-12-23 Interlake, Inc. Apparatus and method for applying plastic strap
US4313779A (en) 1979-07-30 1982-02-02 Signode Corporation All electric friction fusion strapping tool
ZA804443B (en) 1979-07-30 1981-07-29 Signode Corp All electric friction fusion strapping tool
US4535730A (en) * 1980-12-08 1985-08-20 Allen Dillis V Rocker engine
DE3118710A1 (de) 1981-05-12 1982-12-09 Cyklop International Emil Hoffmann KG, 5000 Köln Vorrichtung zum spannen, verschliessen und abschneiden von kunststoffbaendern fuer packstueckumreifungen
DE3220446A1 (de) 1982-05-29 1984-01-26 Hoesch Werke Ag, 4600 Dortmund Vorschub- und spannvorrichtung fuer ein um ein packstueck zu spannendes umreifungsband
KR880002177B1 (ko) 1982-11-15 1988-10-17 마쓰소노 히사미 산성유(乳) 음료의 제조법
DE3332258A1 (de) 1983-09-07 1985-03-21 Trumpf GmbH & Co, 7257 Ditzingen Motorbetriebene handmaschine mit zweiteiligem werkzeug, insbesondere zum stanzen
GB2185228B (en) 1983-09-20 1987-12-09 Bowthorpe Hellermann Ltd Automatic tie gun
US4572064A (en) 1984-05-23 1986-02-25 Burton R Edward Brush bundling system
DE3525647A1 (de) 1984-11-17 1987-01-29 Signode Corp Steuerung der spannvorrichtung zur entlastung des packbandes in einem umreifungsautomaten
US4707390A (en) 1986-06-06 1987-11-17 Signode Corporation Thermoplastic strap weld with encapsulated cavities
US4776905A (en) 1986-06-06 1988-10-11 Signode Corporation Method and apparatus for producing a welded joint in thermoplastic strap
JPS646555A (en) 1987-06-27 1989-01-11 Canon Kk Driving power transmitting device
GB8812292D0 (en) 1988-05-24 1988-06-29 Black & Decker Inc Improvements in/relating to power tools
RU1772784C (ru) 1989-11-04 1992-10-30 Опытное Конструкторско-Технологическое Бюро С Опытным Производством Института Металлофизики Ан Усср Устройство дл автоматического управлени приводом
DE4014307C2 (de) 1990-05-04 1996-11-07 Rmo Systempack Gmbh Packmaschine
DE4014305C2 (de) 1990-05-04 1996-07-18 Rmo Systempack Gmbh Vorrichtung zum Verbinden von sich überlappenden Abschnitten eines thermoplastischen Bandes
US5133532A (en) 1990-10-11 1992-07-28 Illinois Tool Works Inc. Method and apparatus for controlling tension in a strap loop
US5146847A (en) 1991-04-01 1992-09-15 General Motors Corporation Variable speed feed control and tensioning of a bander
US5165532A (en) 1991-05-29 1992-11-24 Westinghouse Electric Corp. Circuit breaker with interlock for welding contacts
US5159218A (en) 1991-07-09 1992-10-27 Allied-Signal Inc. Motor with integral controller
DE4204420A1 (de) 1992-02-14 1993-08-19 Fein C & E Akkumulatorbetriebenes elektrowerkzeug
JP2857280B2 (ja) 1992-06-10 1999-02-17 ストラパック株式会社 梱包機におけるバンド供給・引締方法及び装置
JP3044132B2 (ja) 1992-07-20 2000-05-22 ストラパック株式会社 梱包機におけるバンド接着方法及びその装置
IT1256240B (it) 1992-12-23 1995-11-29 Sestese Off Mec Dispositivo di controllo del trascinamento della reggia in una macchina reggiatrice
GB9320181D0 (en) 1993-09-30 1993-11-17 Black & Decker Inc Improvements in and relating to power tools
DE9316072U1 (de) 1993-10-21 1994-01-05 Cyklop GmbH, 50996 Köln Vorrichtung zum Spannen und Verschließen von Umreifungsbändern
ATE149443T1 (de) 1994-01-24 1997-03-15 Orgapack Ag Spann- und verschliessvorrichtung zum umreifen eines gegenstandes mit einem kunststoffband
US5516022A (en) 1994-02-28 1996-05-14 Illinois Tool Works, Inc. Method and apparatus for a two speed strap take up
JPH07300108A (ja) 1994-05-09 1995-11-14 Kioritz Corp 梱包機
BR9508125A (pt) 1994-06-24 1997-08-12 Talon Ind Llc Aparelho e processo para amarrar um arame em torno de pelo menos um objeto
JPH08258808A (ja) 1995-03-24 1996-10-08 Kioritz Corp 梱包機
US5632851A (en) 1995-04-05 1997-05-27 Pantech International, Inc. Portable article strapping apparatus
ATE195476T1 (de) 1995-05-26 2000-09-15 Orgapack Gmbh Spann- und verschliessvorrichtung zum umreifen eines gegenstandes mit einem kunststoffband
CA2176636A1 (en) 1995-05-26 1996-11-27 Nikolaus Stamm Tensioning and sealing apparatus for strapping an object with a band
JP3702911B2 (ja) 1996-02-02 2005-10-05 横浜ゴム株式会社 空気入りラジアルタイヤ
JP3286524B2 (ja) 1996-04-15 2002-05-27 三洋電機株式会社 バッテリパック
US5798596A (en) 1996-07-03 1998-08-25 Pacific Scientific Company Permanent magnet motor with enhanced inductance
JP3227693B2 (ja) 1996-08-02 2001-11-12 マックス株式会社 鉄筋結束機におけるワイヤのねじ切れ防止方法
CN2266566Y (zh) 1996-09-14 1997-11-05 泛源股份有限公司 手提式捆绑机
US5809873A (en) 1996-11-18 1998-09-22 Ovalstrapping, Inc. Strapping machine having primary and secondary tensioning units and a control system therefor
US5941360A (en) 1996-11-21 1999-08-24 Snap-On Technologies, Inc. Impulse wrench with wrap spring clutch assembly
RU2161773C2 (ru) 1996-12-14 2001-01-10 Владимир Федотович Русинов Устройство для определения угла
US5916108A (en) 1997-05-08 1999-06-29 Bedford Industries, Inc. Device and method for applying a tie ribbon to an aritcle
DE19751861A1 (de) 1997-06-26 1999-01-07 Dieter Bohlig Elektrische Antriebseinrichtung zur Steuerung von Bewegungsvorgängen
US5853524A (en) 1997-06-26 1998-12-29 Illinois Tool Works Inc. Pneumatic circuit for strapping tool having adjustable tension control
US5954899A (en) 1998-04-03 1999-09-21 Illinois Tool Works Inc. Strap welding tool with base plate for reducing strap column strength and method therefor
CN2346694Y (zh) 1998-05-04 1999-11-03 张捷晃 一种新型的携带式电动捆扎机
US6003578A (en) 1998-05-04 1999-12-21 Chang; Jeff Chieh Huang Portable electrical wrapping apparatus
JP3054566U (ja) * 1998-05-20 1998-12-08 捷晃 張 携帯式電動バンド掛機
DE59907362D1 (de) 1998-10-29 2003-11-20 Orgapack Gmbh Dietikon Umreifungsgerät
EP0997377B1 (de) 1998-10-29 2003-09-17 Orgapack GmbH Umreifungsgerät
ATE237500T1 (de) * 1998-10-29 2003-05-15 Orgapack Gmbh Umreifungsgerät
JP3242081B2 (ja) 1998-12-11 2001-12-25 鋼鈑工業株式会社 ストラップ引締溶着工具
US6073664A (en) 1999-02-13 2000-06-13 Illinois Tool Works Inc. Strap tensioning tool
DE19909620A1 (de) 1999-03-05 2000-09-07 Cyklop Gmbh Vorrichtung zum Spannen und Verschließen von Umreifungsbändern
US6173747B1 (en) 1999-03-24 2001-01-16 Illinois Tool Works Inc. Tensioning tool with biased collar valve actuator and method therefor
US6079457A (en) 1999-04-09 2000-06-27 Illinois Tool Works Inc. Sealless strapping tool and method therefor
US6260337B1 (en) 1999-10-27 2001-07-17 Illinois Tool Works Inc. Hand strapping tool
US6206053B1 (en) 1999-11-01 2001-03-27 Panduit Corp. Cable tie tensioning and severing tool
US6415712B1 (en) 1999-12-02 2002-07-09 Enterprises International, Inc. Track mechansim for guiding flexible straps around bundles of objects
US6584891B1 (en) 2000-03-15 2003-07-01 Enterprises International, Inc. Apparatus and methods for wire-tying bundles of objects
DE10026197A1 (de) * 2000-05-26 2001-12-06 Cyklop Gmbh Vorrichtung zum Spannen und Verschließen von Umreifungsbändern
DE10026198A1 (de) * 2000-05-26 2001-11-29 Cyklop Gmbh Vorrichtung zum Spannen und Verschließen von Kunststoff-Umreifungsbändern
US6533013B1 (en) 2000-06-02 2003-03-18 Illinois Tool Works Inc. Electric strapping tool and method therefor
AU6378001A (en) 2000-06-06 2001-12-17 Kim Michael Jensen A method and an apparatus for twisting and tightening a wire
US6308745B1 (en) 2000-06-21 2001-10-30 Illinois Tool Works Inc. Manually-operated sealing tool for joining end portions of plastic strapping, seal member, and sealed joint formed thereby
US6568158B2 (en) * 2000-07-31 2003-05-27 Strapack Corporation Band-applying apparatus and method for use in packing system
US6405766B1 (en) 2000-11-29 2002-06-18 Eaton Corporation Noise dampened float type fuel vapor vent valve
DE10065356C1 (de) 2000-12-27 2002-09-12 Gkn Automotive Gmbh Elektromechanische Drehmomentregelung - Beschleunigung des Rücklaufs
US20020134811A1 (en) 2001-01-29 2002-09-26 Senco Products, Inc. Multi-mode power tool utilizing attachment
JP3699048B2 (ja) 2001-02-01 2005-09-28 ハン イル エ ワ カンパニーリミテッド 物品装着用クリップ
US6554030B2 (en) 2001-03-19 2003-04-29 Illinois Tool Works Inc. Progressive punch
US6422272B1 (en) 2001-04-04 2002-07-23 Illinois Tool Works Inc. Strap sealer with fast-acting dual action piston
EP1260439B1 (de) 2001-05-21 2004-11-17 Orgapack GmbH Umreifungsgerät mit austauschbaren Verschleissteilen
NZ519013A (en) 2001-05-21 2003-05-30 Orgapack Gmbh Manually actuated strapping unit for wrapping a steel strap around a packaged item
NZ519012A (en) 2001-05-21 2003-10-31 Orgapack Gmbh Manually actuated strapping unit for wrapping a steel strap around a packaged item
US6772798B2 (en) 2001-05-25 2004-08-10 Illinois Tool Works, Inc. Strapping tool
DE10146460A1 (de) * 2001-09-20 2003-04-17 Cyklop Gmbh Vorrichtung zum Spannen und Verschließen von Umreifungsbändern
JP2003170906A (ja) 2001-09-28 2003-06-17 Strapack Corp 梱包方法および梱包機
ATE380127T1 (de) 2001-10-15 2007-12-15 Antolin Grupo Ing Sa Zubehörbefestigungssystem für fahrzeuginnenräume
JP2003231291A (ja) 2002-02-07 2003-08-19 Fujitsu Component Ltd サーマルプリンタ
DE10218135B4 (de) * 2002-04-23 2006-07-27 Titan Umreifungstechnik Gmbh & Co Kg Vorrichtung zum Umreifen von Warenstücken mit Band
JP4345260B2 (ja) 2002-05-20 2009-10-14 パナソニック株式会社 付加機能付電動工具
ATE364553T1 (de) 2002-05-24 2007-07-15 Orgapack Gmbh Stanzwerkzeug für ein umreifungsgerät
JP2003348899A (ja) 2002-05-27 2003-12-05 Matsushita Electric Ind Co Ltd モ−タの制御方法及び制御装置
US6907717B2 (en) 2002-06-14 2005-06-21 Illinois Tool Works, Inc. Dual motor strapper
JP2005534199A (ja) 2002-07-26 2005-11-10 ローベルト　ボツシユ　ゲゼルシヤフト　ミツト　ベシユレンクテル　ハフツング Ｇｍｒセンサエレメントおよびｇｍｒセンサエレメントの使用
US20040050188A1 (en) 2002-09-13 2004-03-18 Sparky Industries, Inc. Portable sensor
ES2283737T3 (es) 2002-10-25 2007-11-01 Orgapack Gmbh Conjunto flejador.
US7157882B2 (en) 2002-11-22 2007-01-02 Milwaukee Electric Tool Corporation Method and system for battery protection employing a selectively-actuated switch
US6732638B1 (en) 2003-01-15 2004-05-11 Illinois Tool Works, Inc. Time-out indicator for pneumatic strapper
JP2004241150A (ja) 2003-02-03 2004-08-26 Yuasa Corp 電池
US6911799B2 (en) 2003-04-25 2005-06-28 Illinois Tool Works, Inc. Strapping machine weld motor control system
DE10345135A1 (de) 2003-09-29 2005-04-21 Bosch Gmbh Robert Akkuschrauber
DE20321137U1 (de) 2003-09-29 2006-01-12 Robert Bosch Gmbh Akkuschrauber
JP2004108593A (ja) 2003-12-18 2004-04-08 Osaka Kakuta Kogyo Kk トグルクランプ
ES2290843T3 (es) 2004-02-13 2008-02-16 Thomas & Betts International, Inc. Contador de ciclos para herramienta de instalacion de sujeta-cables.
US7236243B2 (en) 2004-04-12 2007-06-26 Michael Thomas Beecroft Hand-held spectrometer
JP2006000993A (ja) 2004-06-21 2006-01-05 Maeda Metal Industries Ltd 反力受け付き締付機
TWI322783B (en) 2004-11-04 2010-04-01 Orgapack Gmbh A friction welding equipment for a packaging machine
US20060108180A1 (en) 2004-11-24 2006-05-25 Lincoln Industrial Corporation Grease gun
US7073431B1 (en) * 2005-05-18 2006-07-11 Yu-Fu Chen Structure portable strapping machine
US7155885B1 (en) 2005-06-28 2007-01-02 Illinois Tool Works, Inc. Small profile strapping tool
DE102005049130A1 (de) 2005-10-14 2007-04-19 Robert Bosch Gmbh Handwerkzeugmaschine
CA2527162A1 (en) 2005-11-16 2007-05-16 Traction Technologies Inc. Self-tensioning tie down assembly
US7556129B2 (en) 2005-12-14 2009-07-07 Illinois Tool Works, Inc, Motor brake
US7455080B2 (en) 2006-01-26 2008-11-25 Illinois Tool Works Inc. Manual tensioner for non-metallic straps
DE102006007990A1 (de) 2006-02-21 2007-08-30 Robert Bosch Gmbh Handwerkzeugmaschine
KR200419048Y1 (ko) 2006-03-17 2006-06-16 엘에스산전 주식회사 배선용 차단기
JP4961808B2 (ja) 2006-04-05 2012-06-27 マックス株式会社 鉄筋結束機
US7350543B2 (en) 2006-05-09 2008-04-01 Illinois Tool Works Inc. Reduced force sealless connection mechanism
JP2008055563A (ja) 2006-08-31 2008-03-13 Matsushita Electric Works Ltd 電動工具
ES2393573T3 (es) 2007-02-14 2012-12-26 Orgapack Gmbh Dispositivo de flejado
US7866904B2 (en) 2007-03-06 2011-01-11 Datacard Corporation Desktop card printer with indent printing apparatus and method of printing
US7497068B2 (en) 2007-07-10 2009-03-03 Illinois Tool Works Inc. Two-piece strapping tool
CN101164416B (zh) 2007-10-15 2010-06-02 嘉兴市威尔美尼机械制造有限公司 高速线扎机
US8584973B2 (en) 2007-10-31 2013-11-19 Nordson Corporation Powder coating gun with manually operated controls on gun
US8356641B2 (en) 2007-11-02 2013-01-22 Band-It-Idex, Inc. Stationary band clamping apparatus
US7562620B1 (en) 2008-01-30 2009-07-21 Illinois Tool Works, Inc. Strapping tool
RU2355821C1 (ru) 2008-04-11 2009-05-20 Закрытое акционерное общество Фирма "Автоконинвест" Состав для защиты металлов от коррозии и солеотложений
US9284080B2 (en) 2008-04-23 2016-03-15 Signode Industrial Group Llc Mobile strappiing device
US9315283B2 (en) 2008-04-23 2016-04-19 Signode Industrial Group Llc Strapping device with an energy storage means
CN201411061Y (zh) 2008-04-23 2010-02-24 奥格派克有限公司 带有传动装置的捆扎设备
ES2861948T3 (es) 2008-04-23 2021-10-06 Signode Int Ip Holdings Llc Dispositivo de flejado con un accionamiento eléctrico
US10518914B2 (en) * 2008-04-23 2019-12-31 Signode Industrial Group Llc Strapping device
US8567310B2 (en) 2008-07-17 2013-10-29 Xiaojie Yi Electric hand-held binding apparatus
US9061392B2 (en) 2008-07-25 2015-06-23 Sylvain Forgues Controlled electro-pneumatic power tools and interactive consumable
CN101486329B (zh) 2009-02-13 2012-02-22 浙江双友物流器械股份有限公司 捆绑器
CN101585244A (zh) 2009-03-25 2009-11-25 张瑞东 一种双电机电动打包机
ATE530449T1 (de) 2009-04-24 2011-11-15 Sund Birsta Ab Umreifungseinheit und verfahren
USD653923S1 (en) 2009-10-30 2012-02-14 Illinois Tool Works Inc. Tool
USD629321S1 (en) 2009-10-30 2010-12-21 Illinois Tool Works Inc. Control panel for tool
USD651498S1 (en) 2009-10-30 2012-01-03 Illinois Tool Works Inc. Tool
DE102009047443B4 (de) 2009-12-03 2024-04-11 Robert Bosch Gmbh Handwerkzeugmaschine
US8919174B2 (en) 2010-03-12 2014-12-30 Signode Industrial Group Llc Front action sealing tool
US8707785B2 (en) 2010-04-16 2014-04-29 U.E. Systems, Inc. On-board ultrasonic frequency spectrum and image generation
US9296501B2 (en) 2010-07-22 2016-03-29 Signode Industrial Group Llc Modular strap feeder with motor for indexing and gripping
US8281711B2 (en) 2011-01-04 2012-10-09 Illinois Tool Works Inc. Modular feed head with reversing motor
CN201957492U (zh) 2011-01-18 2011-09-07 苏州金莱克精密机械有限公司 具有改进型扳机的手持式电动工具
US8967217B2 (en) * 2011-02-22 2015-03-03 Signode Industrial Group Llc Hand-held strapper
US20140008090A1 (en) 2011-03-31 2014-01-09 Ingersoll-Rand Company Handheld Power Tools with Triggers and Methods for Assembling Same
WO2012134469A1 (en) 2011-03-31 2012-10-04 Ingersoll-Rand Company Display assemblies having integrated display covers and light pipes and handheld power tools and methods including same
CN202100012U (zh) 2011-05-30 2012-01-04 袁炽坤 多功能钢筋绑扎机
GB2481724B (en) 2011-07-13 2012-10-03 Chien-Fa Lai Feeding and reversing mechanism for a strapping machine
US9272799B2 (en) 2011-10-04 2016-03-01 Signode Industrial Group Llc Sealing tool for strap
US8960323B2 (en) 2011-10-18 2015-02-24 Robert Bosch Gmbh Semi-active anti-vibration systems for handheld electrical power tools
CH705745A2 (de) 2011-11-14 2013-05-15 Illinois Tool Works Umreifungsvorrichtung.
CH705744A2 (de) 2011-11-14 2013-05-15 Illinois Tool Works Umreifungsvorrichtung.
CH705743A2 (de) 2011-11-14 2013-05-15 Illinois Tool Works Umreifungsvorrichtung.
DE102011122157A1 (de) 2011-12-23 2013-06-27 Fromm Holding Ag Umreifungsgerät
US9221567B2 (en) * 2012-01-25 2015-12-29 Southern Bracing Systems Enterprises, Llc Systems, methods, and devices for tensioning straps
US9387573B2 (en) 2012-06-07 2016-07-12 Signode Industrial Group Llc Symmetrical overlapping jaw front action sealing tool
US9468968B2 (en) 2012-08-30 2016-10-18 Signode Industrial Group Llc Battery powered tensioning tool for strap
JP6329151B2 (ja) 2012-09-24 2018-05-23 シグノード インターナショナル アイピー ホールディングス エルエルシー バンド掛け装置
EP2711301B1 (en) 2012-09-24 2016-11-02 S.I.A.T. SOCIETA' INTERNAZIONALE APPLICAZIONI TECNICHE S.p.A. Mobile strapping device
CH708294A2 (de) 2013-05-05 2014-12-15 Orgapack Gmbh Umreifungsvorrichtung.

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6109325A (en) * 1999-01-12 2000-08-29 Chang; Jeff Chieh Huang Portable electrical binding apparatus
DE10026200A1 (de) * 2000-05-26 2001-11-29 Cyklop Gmbh Vorrichtung zum Spannen von Umreifungsbändern
WO2009129636A1 (de) * 2008-04-23 2009-10-29 Orgapack Gmbh Umreifungsvorrichtung mit einer spanneinrichtung
DE202011050797U1 (de) * 2011-07-22 2011-11-11 Pantech International Inc. Kipphebelanordnung einer Umreifungsmaschine

Also Published As

Publication number Publication date
US11932430B2 (en) 2024-03-19
CN104870315A (zh) 2015-08-26
JP2015529179A (ja) 2015-10-05
US20230145839A1 (en) 2023-05-11
WO2014072775A8 (de) 2015-05-07
WO2014167377A1 (de) 2014-10-16
CH707028A2 (de) 2014-03-31
US11667417B2 (en) 2023-06-06
JP6329151B2 (ja) 2018-05-23
EP2897867A1 (de) 2015-07-29
US20230264842A1 (en) 2023-08-24
EP2897867B1 (de) 2019-07-31
US9932135B2 (en) 2018-04-03
EP2897866A1 (de) 2015-07-29
JP2015529178A (ja) 2015-10-05
CN105324310A (zh) 2016-02-10
US11267596B2 (en) 2022-03-08
WO2014072775A1 (de) 2014-05-15
JP6412003B2 (ja) 2018-10-24
CN104870315B (zh) 2017-10-10
US20150210411A1 (en) 2015-07-30
US10370132B2 (en) 2019-08-06
ES2895662T3 (es) 2022-02-22
US20180194497A1 (en) 2018-07-12
US20220185517A1 (en) 2022-06-16
US20240199253A1 (en) 2024-06-20
US20150246739A1 (en) 2015-09-03
CH707027A2 (en) 2014-03-31
ES2752195T3 (es) 2020-04-03
US9938029B2 (en) 2018-04-10
US11560245B2 (en) 2023-01-24
US20190300214A1 (en) 2019-10-03
CN105324310B (zh) 2018-03-27

Similar Documents

Publication Publication Date Title
EP2897866B1 (de) Umreifungsvorrichtung mit einer schwenkbaren wippe
CH708294A2 (de) Umreifungsvorrichtung.
EP0999132B1 (de) Umreifungsgerät
EP0997377B1 (de) Umreifungsgerät
DE2720027C3 (de) Bindewerkzeug zum Verdrillen der freien Enden eines Bindedrahtes
EP1283797B1 (de) Vorrichtung zum spannen von umreifungsbändern
EP0999133B1 (de) Umreifungsgerät
DE2700533C3 (de) Vorrichtung zur Bildung einer gespannten Bandschlaufe um eine Verpackung
DE1536270C2 (de) Vorrichtung zum Umschnüren von Gegenständen
DD202269A5 (de) Vorrichtung zum spannen, verschliessen und abschneiden von kunststoffbaendern fuer packstueckumreifungen
DE3028729A1 (de) Umschuerungsgeraet
CH712984A2 (de) Umreifungsvorrichtung zur Umreifung von Packgut mit einem Umreifungsband.
EP3105126B1 (de) Spanneinrichtung für eine umreifungsvorrichtung
EP0894718B1 (de) Bandschiebeeinrichtung einer Umreifungsmaschine
EP0357902B1 (de) Spann- und Verschliessgerät für ein Umreifungsband aus Kunststoff
DE3819135C1 (ja)
EP3556667B1 (de) Umreifungsvorrichtung
DE719423C (de) Vorrichtung zum Zusammenbinden von gebuendelten Briefen, Schriftstuecken, Gegenstaenden u. dgl.
DE1945837C (de) Vorrichtung zum Umschnüren einer Packung
DE1586827C (de) Vorrichtung zum selbsttätigen Span nen des Verpackungsbandes bei Verschnür maschinen
DE1923907C3 (de) Vorrichtung zum Verschweißen von sich teilweise überlappenden Bändern aus thermoplastischem Material mittels Reibungswärme
DE281799C (ja)
DE1586502C (de) Spannvorrichtung für Bander, insbe sondere aus Kunststoff, Textilien u dgl
DE566004C (de) Vorrichtung zum Umschnueren von Kisten, Ballen o. dgl. mit Draht
EP0415272A1 (de) Anordnung an einem Umreifungsgerät zum Spannen einer um einen zu umreifenden Gegenstand gelegten Schlaufe

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20150423

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

DAX Request for extension of the european patent (deleted)
STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: EXAMINATION IS IN PROGRESS

17Q First examination report despatched

Effective date: 20171207

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE

PUAG Search results despatched under rule 164(2) epc together with communication from examining division

Free format text: ORIGINAL CODE: 0009017

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: EXAMINATION IS IN PROGRESS

17Q First examination report despatched

Effective date: 20181207

B565 Issuance of search results under rule 164(2) epc

Effective date: 20181207

RIC1 Information provided on ipc code assigned before grant

Ipc: B65B 13/02 20060101ALI20181204BHEP

Ipc: B65B 13/18 20060101ALI20181204BHEP

Ipc: B65B 13/32 20060101ALI20181204BHEP

Ipc: B65B 13/22 20060101AFI20181204BHEP

TPAC Observations filed by third parties

Free format text: ORIGINAL CODE: EPIDOSNTIPA

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: EXAMINATION IS IN PROGRESS

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: GRANT OF PATENT IS INTENDED

INTG Intention to grant announced

Effective date: 20210215

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE PATENT HAS BEEN GRANTED

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 1416764

Country of ref document: AT

Kind code of ref document: T

Effective date: 20210815

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502013015866

Country of ref document: DE

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REG Reference to a national code

Ref country code: SE

Ref legal event code: TRGR

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG9D

REG Reference to a national code

Ref country code: NL

Ref legal event code: FP

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210804

Ref country code: RS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210804

Ref country code: NO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20211104

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20211206

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210804

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20211104

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210804

REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2895662

Country of ref document: ES

Kind code of ref document: T3

Effective date: 20220222

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210804

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210804

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20211105

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210804

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502013015866

Country of ref document: DE

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20210930

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SM

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210804

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210804

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210804

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210804

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210804

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210804

Ref country code: AL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210804

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20220506

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20210924

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20210924

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20210930

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210804

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 1416764

Country of ref document: AT

Kind code of ref document: T

Effective date: 20210924

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20210924

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO

Effective date: 20130924

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210804

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20230921

Year of fee payment: 11

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: SE

Payment date: 20230927

Year of fee payment: 11

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: ES

Payment date: 20231002

Year of fee payment: 11

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: CH

Payment date: 20231004

Year of fee payment: 11

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210804

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: NL

Payment date: 20240820

Year of fee payment: 12

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210804

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20240820

Year of fee payment: 12

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20240822

Year of fee payment: 12

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20240820

Year of fee payment: 12