EP2285691B1 - Umreifungsvorrichtung mit einer spanneinrichtung - Google Patents

Umreifungsvorrichtung mit einer spanneinrichtung Download PDF

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Publication number
EP2285691B1
EP2285691B1 EP09735814.7A EP09735814A EP2285691B1 EP 2285691 B1 EP2285691 B1 EP 2285691B1 EP 09735814 A EP09735814 A EP 09735814A EP 2285691 B1 EP2285691 B1 EP 2285691B1
Authority
EP
European Patent Office
Prior art keywords
tensioning
compensator
strapping
band
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
EP09735814.7A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP2285691A1 (de
Inventor
Mirco Neeser
Roland Widmer
Flavio Finzo
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
Premark Packaging 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
Application filed by Premark Packaging LLC filed Critical Premark Packaging LLC
Publication of EP2285691A1 publication Critical patent/EP2285691A1/de
Application granted granted Critical
Publication of EP2285691B1 publication Critical patent/EP2285691B1/de
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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
    • B65B13/24—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
    • 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
    • B65B13/187—Motor means

Definitions

  • the invention relates to a strapping device, in particular mobile strapping device, for strapping packaged goods with a strapping, which has a clamping device for applying a belt tension on a loop of a strapping, a rotatably driven tensioning wheel and a pivotable relative to the tensioning wheel and cooperating with the tensioning wheel rocker, wherein a clamping plate for supporting a strapping band is arranged on the tensioning rocker, and a distance between the tensioning plate and the tensioning wheel for applying a tensioning force to the band is changeable, and a connecting device, in particular a welding device such as a friction welding device, for establishing a connection on two superimposed areas the loop of the strapping, has.
  • a connecting device in particular a welding device such as a friction welding device
  • a strapping device in which a pivotable rocker can be pressed with a mounted on the rocker smooth clamping plate by means of a lever in the direction of the tensioning wheel of the strapping direction, for example, from the EP 0 480 627 A1 out.
  • a rocker In the EP 0 997 377 A1 however, a rocker is pivotally mounted on a rigid base plate. On the rocker there are two counter-rollers, against which the band rests during the clamping process by means of the clamping device.
  • the US 4 015 643 discloses a strapping device in which in addition to the pivoting of the tensioning wheel, a variability of the relative position of the clamping plate with respect to the tensioning wheel can be generated by pivoting the clamping plate to compensate for different belt thicknesses.
  • Umrelfungsvoriquesen a rotatably drivable tensioning wheel cooperates with a toothed and usually concave clamping plate, which is arranged on a pivotable rocker.
  • the rocker can be pivoted for the purpose of applying a clamping force on a belt loop in the direction of the tensioning wheel and pressed against the tensioning wheel.
  • a pivot axis of the rocker does not coincide in this rule with the axis of rotation of the tensioning wheel.
  • the strapping device has a Reibschwei worn with which the belt loop in the region of the two superimposed band layers in the strapping device can be heated by means of an oscillating moving Reibschweisselements so far that the plastic tape melts locally, the material of the two band layers flows into each other and cohesively cohesively with each other combines.
  • the invention is therefore an object of the invention to provide a strapping device of the type mentioned, with the same possible good clamping properties are achieved even with different tape thicknesses.
  • a fluctuating sand tension is essentially due to the fact that the position of the clamping plate changes with respect to the tensioning wheel.
  • the invention therefore provides means for compensating the displacement of the intervention sites.
  • This at least one means is a relative mobility of the clamping plate relative to the clamping rocker by a floating mounting of the clamping plate on the Spannwlppe.
  • a variability of the position of the tensioning wheel could be provided in relation to the pivot axis of the rocker.
  • the proposed relative mobility of the clamping plate with respect to the rocker should be given in particular with respect to a direction by which a position of the clamping plate relative to the circumference of the tensioning wheel can be changed.
  • This direction corresponds at least approximately to the longitudinal direction along which a strapping band inserted into the strapping device extends within the strapping device or the direction along which the straining plate moves due to the rocker movement.
  • Such an embodiment has the advantage that the contact pressure, in particular a substantially uniformly distributed contact pressure, is made possible by the clamping plate on the band or band on the tensioning wheel, regardless of the respective band thickness over substantially the entire length of the clamping plate.
  • the engagement conditions can be further improved even for different strip thicknesses alternatively or in addition to the mobility of the clamping plate in that the clamping plate is concavely curved with a radius that advantageously at least approximately corresponds to the outer radius of the tensioning wheel or can be slightly larger.
  • a concave configuration of the clamping surface helps during clamping between the clamping surface of the clamping plate and the outer surface of the tensioning wheel over preferably the entire length of the clamping surface - with respect to the clamping direction - to provide a gap with at least approximately constant gap height.
  • the clamping plate can be substantially always aligned so that over the entire length of the clamping plate, a gap results in substantially constant gap height, at least with a lower gap height variation than in conventional solutions. This allows over the entire length of the clamping plate a more uniform pressure application to the strapping band than before.
  • the solution according to the invention shows in particular strong in small packages (edge length of about 750mm and smaller) and in round packages (diameter about 500mm - 1000mm) in conjunction with high clamping forces advantages.
  • the then relatively small belt loop when tightening to a shock-like load of the lower belt layer, ie the end of the tape, out, through which the lower belt ply is pulled against the clamping plate. Due to very different pressure conditions over the entire length of the clamping plate, a secure holding of the band end in the strapping device could not be guaranteed in previous solutions.
  • the movable clamping plate has here decisive advantages, which are essentially in the fact that even with shock-like clamping loads in conjunction with high clamping forces, the bands can be held by the optimal due to their mobility aligned tooth plate.
  • the relative mobility of the clamping plate can be realized by a bearing of the clamping plate on the rocker using non-mutually parallel bearing surfaces of the clamping plate.
  • the clamping plate is provided with a convex contact surface which rests on a substantially flat support surface of the rocker. This allows a tilting of the clamping plate, whereby a self-alignment and nestling of the clamping plate can be made to the periphery of the tensioning wheel.
  • measures can also be provided by which a self-alignment of the clamping plate in a direction transverse to the strip can be achieved. Such a measure may for example be a convex course of the bearing surface of the clamping plate and transverse to the belt.
  • a further advantageous embodiment according to the invention can provide that the clamping plate is provided with a guide, which results in a mobility in one or more predetermined directions.
  • the guiding direction may in particular be a direction which is aligned at least substantially parallel to the strip course within the strapping device.
  • the guide for the clamping plate by means of a slot and a guide means arranged therein, such as a screw can be formed.
  • exclusively hand-operated inventive strapping device 1 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 apparatus is further provided with a base plate 4, the underside of which is provided for placement on an object to be packaged. On the base plate 4 and connected to the base plate not shown carrier of the strapping device all functional units of the strapping device 1 are attached.
  • the clamping device has for this purpose a tensioning wheel 7, with which the band can be detected for a clamping operation.
  • the tensioning wheel 7 acts together with a rocker 8, which can be pivoted by means of a rocker arm 9 from an end position with distance to the tensioning wheel in a second end position about a rocker pivot axis 8a, in which the rocker 8 is pressed against the tensioning wheel 7.
  • a welding of the two layers by means of the friction-welding device 8 of the strapping device can take place at one point of the belt loop on which two layers of the belt lie one above the other.
  • the strap loop can thereby be permanently closed.
  • the friction-welding device 10 is provided with a welding shoe 11, which melts the two layers of the strapping band by mechanical pressure on the strapping band and a simultaneous oscillating movement with a predetermined frequency.
  • the plasticized or molten areas flow into each other and after cooling of the band then creates a connection between the two band layers. If necessary, then the belt loop can be separated from a supply roll of the tape by means of a cutting device of the strapping device 1, not shown.
  • the actuation of the tensioning device 6, the delivery of the friction-welding device 10 by means of a transfer device 19 (FIG. Fig. 6 ) of the friction-welding device 10 as well as the use of the friction-welding device per se and the operation of the cutting device are carried out using only a common electric motor 14, which provides a drive movement for each of these components.
  • a supply of other external auxiliary energy, such as compressed air or other electricity, is in the strapping apparatus according to the Fig. 1 and 2 not provided.
  • the portable mobile strapping device 1 has a trained as a pressure switch actuator 16, which is provided for commissioning of the motor.
  • actuating element 16 17 three modes can be adjusted by means of a switch. In the first mode, both the tensioning device 6 and the friction-welding device 10 are actuated successively and automatically by actuation of the actuating element 16 without the need for further operator activity.
  • the switch 17 is switched to a second switching mode. In the second possible mode, only the tensioning device 6 is then released by actuating the actuating element 16.
  • a second actuating element 18 must be actuated by the operator.
  • the first actuating element 16 is to be actuated a second time.
  • the third mode is a kind of semiautomatic, in which the tension button 16 is to be pressed until the prestressed tension or tensile stress in the belt is reached. In this mode, it is possible to interrupt the clamping process by releasing the tensioning button 16, for example, to attach edge protectors to the Umreifungsgut under the strapping. By pressing the tension button, the clamping process can then be resumed.
  • This third mode can be combined with a separately triggered as well as with an automatically subsequent friction welding process.
  • motor shaft 27 designed as a brushless, grooved female rotor DC motor 14, a transmission device 13 is arranged.
  • the brushless DC motor 14 can be operated in both directions of rotation, with one direction of rotation being used as the drive movement of the clamping device 6 and the other direction of rotation being used as the drive movement of the welding device 10.
  • the in Fig. 4 brushless DC motor 14 shown purely schematically is formed with a grooved internal rotor (rotor) 20 with three Hall sensors HS1, HS2, HS3.
  • This EC motor (electronically commutated motor) has a permanent magnet in its rotor 20 and is provided with an electronic control 22 which is provided for electronic commutation in the stator 24.
  • the electronic controller 22 determines via the Hall sensors HS1, HS2, HS3, which also assume the function of position sensors in the embodiment, the respective instantaneous position of the rotor 20 and switches the electric magnetic field in the windings of the stator 24.
  • the phases are switched in response to the position of the rotor 20 to cause a rotational movement of the rotor in a certain direction of rotation, with a predeterminable variable speed and torque.
  • a so-called "1 quadrant motor drive amplifier” is used, which provides the motor with the voltage, as well as peak and continuous current available and controls.
  • the current flow for not shown coil strands of the stator 24 is controlled by a bridge circuit 25 (MOSFET transistors), ie commutated.
  • a not further shown temperature sensor is provided on the engine. It is thus possible to monitor and control the direction of rotation, the speed of rotation, the current limit and the temperature.
  • the commutation is constructed as a separate print component and accommodated in the strapping device separately from the motor.
  • the power supply is ensured by the trained as a lithium-ion battery accumulator 15.
  • Such rechargeable batteries are based on a number of independent lithium-ion cells, in each of which at least substantially independently chemical processes for generating a potential difference between two poles of the respective cell take place.
  • the battery of the embodiment has eight cells and has a capacity of 2.6 ampere hours.
  • As an active material or as a negative electrode of the lithium-ion battery graphite is provided.
  • the positive electrode of the accumulator often has lithium metal oxides, in particular in the form of layer structures.
  • the electrolyte used is usually anhydrous salts, such as lithium hexafluorophosphate or polymers.
  • the one by one conventional lithium-ion battery delivered voltage is usually 3.6 volts.
  • the energy density of such accumulators is about 100 Wh / kg - 120 Wh / kg.
  • the transmission device 13 has a freewheel 36 arranged on the motor-side drive shaft, on which a sun gear 35 of a first planetary gear stage is arranged.
  • the freewheel 36 is only in one of the two possible directions of rotation of the drive, the rotational movement of the sun gear 35 on.
  • the sun gear 35 meshes with three Planentengan 37, which are in a conventional manner in engagement with a fixed ring gear 38.
  • Each of the planet gears 37 is in turn arranged on a respective shaft 39 associated therewith, which is in each case integrally connected to a driven gear 40.
  • the rotation of the planet gears 37 about the motor shaft 27 results in a rotational movement of the driven gear 40 about the motor shaft 27 and determines a rotational speed of this rotational movement of the output gear 40.
  • the output gear 40 is located on the freewheel 36 and is therefore also on the motor shaft stored.
  • This freewheel 36 causes both the sun gear 35 and the output gear 40 rotate only in one direction of rotation of the rotational movement of the motor shaft 27.
  • the freewheel 29 may for example be of the type INA HFL0615, as offered by the company Schaeffler KG, D-91074 Herzogenaurach.
  • the gear device 13 has on the motor-side output shaft 27 also a belonging to a second planetary gear toothed sun gear 28, through the recess while the shaft 27 is performed, in this case, the shaft 27 is not connected to the sun gear 28.
  • the sun gear is fixed to a disc 34, which in turn is connected to the planetary gears 37.
  • the rotational movement of the planetary gears 37 about the motor-side output shaft 27 is thus transmitted to the disc 34, which in turn transmits its rotational motion identical to the sun gear 28.
  • the sun gear 28 meshes with a plurality of planet gears, namely three, each arranged on a parallel to the motor shaft 27 extending shaft 30 gears 31.
  • the shafts 30 of the three gears 31 are fixedly arranged, ie they do not rotate about the motor shaft 27.
  • the three gears 31 are in turn with an internally toothed ring gear engaged on its outer side has a cam 32 and subsequently as Cam wheel 33 is designated.
  • the sun gear 28, the three gears 31 and the cam 33 are components of the second planetary gear stage.
  • the planetary gear on the input side Rotationsbewegegung the shaft 27 and the rotational movement of the cam wheel 33 are in a ratio of 60: 1, ie by the two-stage planetary gear is a 60-fold reduction takes place.
  • a bevel gear 43 is also arranged on a second freewheel 42, which is in engagement with a second bevel gear, not shown.
  • This freewheel 42 also transmits only in one direction of rotation of the motor shaft 27, the rotational movement.
  • the direction of rotation, in which the freewheel 36 of the sun gear 35 and the freewheel 42 transmit the rotational movement of the motor shaft 27 are opposed to each other. This means that in one direction of rotation rotates only the freewheel 36 and in the other direction only the freewheel 42 with.
  • the second bevel gear is arranged at one end of a clamping shaft, not shown, which carries at its other end another planetary gear 46 ( Fig. 2 ).
  • the drive movement of the electric motor in a certain direction of rotation is thus transmitted to the two bevel gears 43 to the clamping shaft.
  • the tensioning wheel 49 of the tensioning device 6 designed as an internally toothed ring gear is thereby set in rotation.
  • the provided on its outer surface with a surface structure tensioning wheel 7 takes in its rotational movement, the respective strap through a frictional engagement, whereby the intended belt tension is applied to the belt loop.
  • the output gear 40 is formed in the region of its outer peripheral surface as a gear on which a toothed belt 50 of an envelope drive is arranged ( Fig. 5 and Fig. 6 ).
  • the toothed belt 50 also wraps around a relative to the output gear 40 in diameter smaller pinion 51, whose shaft drives an eccentric 52 for an oscillating reciprocating movement of the welding shoe 53.
  • a toothed belt drive and any other form of enveloping drives could be provided, such as a V-belt or chain drive.
  • the eccentric drive 52 has an eccentric shaft 54, on which an eccentric 55 is arranged, on which in turn sits a welding shoe arm 56 with a circular recess.
  • the welding device is further provided with a toggle device 60, by means of which the welding device is moved from a rest position (FIG. Fig. 7 ) in a welding position ( Fig. 9 ) can be transferred.
  • the toggle device 60 is attached to the welding shoe arm 56 and in this case provided with a pivotable on Schweissschuharm 56 longer toggle lever 61.
  • the toggle device 60 is further provided with a pivotable about a pivot axis 62 pivoted pivot member 63 which acts in the toggle lever 60 as a shorter toggle.
  • the pivot axis 62 of the pivot member 63 in this case runs parallel to the axes of the motor shaft 27 and the eccentric shaft 57th
  • the pivotal movement is initiated by means of the cam 32 of the cam wheel 33, which in the counterclockwise rotation in the rotation - based on the representations of Fig. 7 to 9 - the cam wheel 33 passes under the pivot member 63 ( Fig. 8 ).
  • a ramp-like rising surface 32a of the cam 32 in this case touches an inserted into the pivot member 63 contact element 64.
  • the pivot member 63 is thereby rotated clockwise about its pivot axis 62.
  • a two-part longitudinally adjustable toggle lever rod of the toggle lever 61 which is in two parts according to the principle "piston-cylinder", is arranged pivotable about a pivot axis 69.
  • the latter is also rotatably articulated to a pivot axis 65 designed as a further pivot point 65 of the welding shoe arm 56 in the vicinity of the welding shoe 53 and at a distance from the pivot axis 57 of the welding shoe arm 56.
  • a compression spring 67 is arranged on this, by means of which the toggle lever 61 is pressed both against the welding shoe arm 56 and against the pivoting element 63.
  • the pivoting member 63 is thus operatively connected with the toggle lever 61 and the welding shoe arm 56 with respect to its pivotal movements.
  • a toggle lever 61 extending (imaginary) connecting line 68 of the two articulation points of the toggle lever 61 between the pivot axis 62 of the pivot member 63 and the cam wheel 33, ie on one side of the pivot axis 62.
  • the toggle lever 61 is taken from the pivot member 63 with.
  • Fig. 8 an intermediate position of the toggle lever 61 is shown, in which the connecting line 68 of the articulation points 65, 69, the pivot axis 62 of the pivot member 63 intersects.
  • the in the representation of Fig. 6 and 9 counterclockwise driving movement of the electric motor is transmitted from the timing belt 50 to the now transferred by the toggle lever 60 in the welding position welding shoe 53, which is pressed on the two band layers and moves back and forth in an oscillating motion.
  • the welding time for generating a Reibschweisstress is determined by the fact that the adjustable number of revolutions of the cam wheel 33 is counted from the time from which the cam 32, the contact element 64 is actuated.
  • the number of revolutions of the shaft 27 of the brushless DC motor 14 is counted to determine the position of the cam wheel 33, from which the engine 14 is turned off and thus the welding process is to be terminated.
  • the described successive processes “clamping” and “welding” can be triggered jointly in a switching state of the actuating element 16.
  • the actuating element 16 is to be actuated once, whereby the electric motor 14 first runs in the first direction of rotation and in this case (exclusively) the tensioning device 6 is driven.
  • the band tension to be applied to the respective band can preferably be set on the strapping apparatus by means of a pushbutton in nine stages which correspond to nine different band tension values. Alternatively, a continuous adjustment of the belt tension could be provided.
  • the applied belt tension can be adjusted in the form of a limit of the motor current via push buttons in nine stages on the control electronics des.Umreifungs réelles.
  • the motor 14 After reaching an adjustable and thus predeterminable limit value for the motor current or for the belt tension, the motor 14 is turned off by its controller 22. Immediately thereafter, the motor is operated by the controller 22 in the reverse direction of rotation. As a result, in the manner described above, the welding shoe 53 is lowered onto the two superposed belt layers and the oscillating movement of the welding shoe is carried out to produce the friction-welded connection.
  • the actuating element 16 can be occupied only with the function of the triggering the clamping device. If such a setting is made, only the clamping device is put into operation by pressing the actuator and turned off again after reaching the preset belt tension. In order to trigger the Reibschweissvorgang the second actuator 18 must be actuated. However, apart from the separate triggering, the function of the friction welding device is identical to the other mode of the first actuating element.
  • rocker 8 by pressing the in the Fig. 2 . 10 . 11 illustrated rocker lever 9 pivoting movements to perform about the rocker axis 8a.
  • the rocker is this purpose by means of a behind the tensioning wheel 7 and therefore in Fig. 2 unrecognizable, rotatable cam moves.
  • the cam can perform a rotational movement of about 30 ° and move the rocker 8 and clamping plate 12 relative to the tensioning wheel 7, which allows insertion of the tape in the strapping or between the tensioning wheel 7 and clamping plate 12.
  • the tensioning wheel 7 facing toothed surface 12a (clamping surface) is concavely curved, wherein the radius of curvature corresponds to the radius of the tensioning wheel 7, or is slightly larger.
  • the toothed clamping plate 12 is arranged in a groove-shaped recess 71 of the rocker.
  • the clamping plate 12 is provided with a convexly curved contact surface 12 b, with which it is mounted in the recess 71 of the rocker 8 on a flat bearing surface 72 is.
  • the clamping plate 12 is able to perform in the position in the band running direction 70 relative to the rocker 8 and the tensioning wheel 7 tilting movements. Furthermore, the clamping plate 12 is fastened to the rocker 8 with a screw 73 carried out from below by the rocker. For this purpose, the screw is located in a slot 74 of the rocker, whose longitudinal extent runs parallel to the band path 70 in the strapping device. The clamping plate 12 is thereby additionally arranged longitudinally displaceable on the rocker 8 in addition to the tiltability.
  • the clamping rocker 8 In a clamping operation, first, the clamping rocker 8 from the rest position ( Fig. 10 ) in the clamping position ( Fig. 11 ). In the clamping position, the spring-loaded rocker 8 presses the clamping plate 12 in the direction of the tensioning wheel and clamps both tape layers between the tensioning wheel 7 and the clamping plate 12. Due to different strip thicknesses, different distances between the clamping plate 12 and the circumferential surface 7a of the tensioning wheel 7 can result. This not only different pivoting positions of the rocker 8 result, but also different position of the clamping plate 12 with respect to the circumferential direction of the tensioning wheel 7.
  • the clamping plate 12 is directed during the pressing of the tape by a longitudinal movement in the recess 71 and a tilting movement on the contact surface 12b on the support surface 72 independently so that the clamping plate 12 exerts over its entire length as uniform as possible pressure on the strapping.
  • the tensioning wheel 7 is turned on, the teeth of the clamping plate 12 holds the lower band position, while the tensioning wheel 7 detects the upper band position with its toothed peripheral surface 7a.
  • the rotation movement the tensioning wheel 7 and the lower coefficient of friction between the two band layers then causes the tensioning wheel to retract the upper band ply and thus increase the tension in the band loop to the desired tension value.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Basic Packing Technique (AREA)
EP09735814.7A 2008-04-23 2009-01-06 Umreifungsvorrichtung mit einer spanneinrichtung Active EP2285691B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH6482008 2008-04-23
PCT/CH2009/000004 WO2009129636A1 (de) 2008-04-23 2009-01-06 Umreifungsvorrichtung mit einer spanneinrichtung

Publications (2)

Publication Number Publication Date
EP2285691A1 EP2285691A1 (de) 2011-02-23
EP2285691B1 true EP2285691B1 (de) 2015-03-11

Family

ID=40451285

Family Applications (1)

Application Number Title Priority Date Filing Date
EP09735814.7A Active EP2285691B1 (de) 2008-04-23 2009-01-06 Umreifungsvorrichtung mit einer spanneinrichtung

Country Status (8)

Country Link
US (1) US9193486B2 (zh)
EP (1) EP2285691B1 (zh)
JP (1) JP2011518088A (zh)
KR (1) KR101613247B1 (zh)
CN (2) CN102026875B (zh)
ES (1) ES2539151T3 (zh)
RU (1) RU2471687C2 (zh)
WO (1) WO2009129636A1 (zh)

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IT201900006288A1 (it) * 2019-04-24 2020-10-24 Itatools S R L Reggiatrice
IT201900006286A1 (it) * 2019-04-24 2020-10-24 Itatools S R L Reggiatrice
EP4001135B1 (en) * 2020-11-12 2023-09-20 Itatools S.r.l. Control mechanism for tilting machine of strapping machine

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JP2011518087A (ja) 2008-04-23 2011-06-23 オルガパック ゲゼルシャフト ミット ベシュレンクテル ハフツング エネルギ貯蔵手段を有するバンド掛け装置
DE102011011627A1 (de) 2011-02-17 2012-08-23 Krones Aktiengesellschaft Vorrichtung und Verfahren zur Herstellung von umreiften Gebinden sowie Regelungs- und/oder Steuerungsverfahren für eine Umreifungsvorrichtung
CN102642632B (zh) * 2011-02-18 2015-08-05 海尔曼太通株式会社 手动型打捆工具
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CH708294A2 (de) * 2013-05-05 2014-12-15 Orgapack Gmbh Umreifungsvorrichtung.
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US9193486B2 (en) 2015-11-24
US20110056392A1 (en) 2011-03-10
KR101613247B1 (ko) 2016-04-18
CN102026875B (zh) 2016-01-20
RU2010147640A (ru) 2012-05-27
KR20100135275A (ko) 2010-12-24
ES2539151T3 (es) 2015-06-26
JP2011518088A (ja) 2011-06-23
CN201411058Y (zh) 2010-02-24
RU2471687C2 (ru) 2013-01-10
WO2009129636A1 (de) 2009-10-29
EP2285691A1 (de) 2011-02-23

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