EXHIBIT 8

Case 2:24-cv-00080-JRG Document 57-9 Filed 10/17/24 Page 1 of 24 PageID #: 1417
US010370132B2 

( 12 ) United States Patent 

Finzo et al . ( 10 ) Patent No . : US 10 , 370 , 132 B2 

( 45 ) Date of Patent : Aug . 6 , 2019 

( 54 ) STRAPPING DEVICE HAVING A ( 58 ) 

PIVOTABLE ROCKER 

Field of Classification Search 

CPC . . . B65B 13 / 025 ; B65B 13 / 187 ; B65B 13 / 322 ; 

B65B 13 / 22 ; B65B 13 / 32 ; B65B 13 / 18 , B65B 13 / 02 

( Continued ) 

( 71 ) Applicant : Signode Industrial Group LLC , Glenview , IL ( US ) 

( 72 ) Inventors : Flavio Finzo , Wurenlos ( CH ) ; Mirco ( 56 ) References Cited 

Neeser , Ehrendingen ( CH ) ; Dimitrios 

Takidis , Dubendorf ( CH ) U . S . PATENT DOCUMENTS 

( 73 ) Assignee : Signode Industrial Group LLC , Glenview , IL ( US ) 

3 , 367 , 374 A 

3 , 654 , 033 A 

2 / 1968 Meier et al . 4 / 1972 Angarola et al . 

( Continued ) 

( * ) Notice : Subject to any disclaimer , the term of this FOREIGN PATENT DOCUMENTS 

patent is extended or adjusted under 35 

U . S . C . 154 ( b ) by 0 days . CA 

CH 

2 432 353 12 / 2003 

705 745 5 / 2013 

( 21 ) Appl . No . : 15 / 910 , 346 ( Continued ) 

( 22 ) Filed : Mar . 2 , 2018 OTHER PUBLICATIONS 

( 65 ) Prior Publication Data 

US 2018 / 0194497 A1 Jul . 12 , 2018 

International Search Report and Written Opinion for International 

Application No . PCT / IB2013 / 002116 dated Jun 30 , 2014 ( 8 pages ) . 

( Continued ) 

Primary Examiner — Jimmy T Nguyen 

( 74 ) Attorney , Agent , or Firm — Neal , Gerber & Eisenberg LLP 

Related U . S . Application Data 

( 62 ) Division of application No . 14 / 430 , 163 , filed as 

application No . PCT / IB2013 / 002116 on Sep . 24 , 2013 , now Pat . No . 9 , 938 , 029 . 

( 30 ) Foreign Application Priority Data 

Sep . 24 , 2012 ( CH ) 1723 / 12 

Sep . 24 , 2012 ( CH ) . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 1724 / 12 

( 51 ) Int . CI . B65B 13 / 02 ( 2006 . 01 ) 

B65B 13 / 22 ( 2006 . 01 ) 

( Continued ) ( 52 ) U . S . CI . CPC . . . . . . . . . . . . . . B65B 13 / 22 ( 2013 . 01 ) ; B65B 13 / 02 

( 2013 . 01 ) ; B65B 13 / 025 ( 2013 . 01 ) ; 

( Continued ) 

( 57 ) ABSTRACT 

Various embodiments of the present disclosure provide a mobile strapping device for strapping packaged products using a loop of wrapping strap . The strapping device 

includes a tensioning device for applying tension to the strap and a connecting device for connecting two overlapping portions of the strap . The tensioning device includes a 

rotatable tensioning wheel and a tensioning plate . The 

tensioning wheel is supported by a rocker that is pivotable to change a distance separating the tensioning wheel and the 

tensioning plate . The mobile strapping device includes a 

motor that is operably connectable to the rocker or the 

tensioning wheel such that the motor causes pivoting of the 

rocker or rotation of the tensioning wheel when operating in 

( Continued ) 

159 

155 143 

- 1170 

152 

158 156 

80c 107 

86a 

1176 1076 80 89 

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US 10 , 370 , 132 B2 

Page 2 

a first direction of rotation . In various embodiments , gear ing , including a plurality of planetary gear sets , is used to 

operatively connect the motor to the rocker and the tension 

ing wheel . 

13 Claims , 10 Drawing Sheets 

( 51 ) Int . Cl . B65B 13 / 18 ( 2006 . 01 ) 

B65B 13 / 32 ( 2006 . 01 ) 

( 52 ) U . S . CI . CPC . . . . . . . . . . . . B65B 13 / 187 ( 2013 . 01 ) ; B65B 13 / 32 

( 2013 . 01 ) ; B65B 13 / 322 ( 2013 . 01 ) 

Field of Classification Search 

USPC . . . . . . . . . . . . . . . 100 / 29 , 32 

See application file for complete search history . 

( 58 ) 

( 56 ) References Cited 

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100 / 2 

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2014 / 0311363 Al 10 / 2014 Leppert 

. . . . . . . . . . . . . . . . . . 

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US 10 , 370 , 132 B2 

Page 3 

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S5638220 

H07300108 

H08258808 

H09283103 

3054566 U 

3044132 

2003231291 

2003 - 534989 

2003348899 

2004108593 

2004241150 

1772784 

2161773 

2355821 

WO 01 / 89929 

WO 2006 / 048738 

WO 2009 / 129633 

WO 2009 / 129636 

1 / 1979 

4 / 1981 

11 / 1995 

10 / 1996 

10 / 1997 

5 / 1998 

5 / 2000 

8 / 2003 

11 / 2003 

12 / 2003 

4 / 2004 

8 / 2004 

10 / 1992 

1 / 2001 

5 / 2009 

11 / 2001 

5 / 2006 

10 / 2009 

10 / 2009 

CN 

CN 

CN 

CN 

CN 

JP 

RU 

RU 

RU 

WO 

WO 

WO 

WO 

CN 

CN 

CN 

DE 

DE 

DE 

DE 

DE 

DE 

DE 

EP 

EP 

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OTHER PUBLICATIONS 

2266566 

1660675 A 

101164416 

100460284 C 

101486329 

101585244 A 

101870367 

202100012 

40 14 305 

4204420 A1 

19751861 

20321137 

10200549130 

10 2006 007990 

202011050797 

0095643 

0603868 

0659525 

0744343 

1177978 

1413519 

1 161 827 

2 041 869 

2 481 724 

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Brushless DC Motor Drives , by Ali Emandi , in Energy - Efficient 

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No . 201380061441 . 6 , dated Feb . 1 , 2016 ( 9 pages ) . 

EP 

EP 

EP 

GB 

GB 

GB * cited by examiner 

Case 2:24-cv-00080-JRG Document 57-9 Filed 10/17/24 Page 4 of 24 PageID #: 1420
U . S . Patent Aug . 6 , 2019 Sheet 1 of 10 US 10 , 370 , 132 B2 

Hool 

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Case 2:24-cv-00080-JRG Document 57-9 Filed 10/17/24 Page 5 of 24 PageID #: 1421
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Case 2:24-cv-00080-JRG Document 57-9 Filed 10/17/24 Page 9 of 24 PageID #: 1425
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Case 2:24-cv-00080-JRG Document 57-9 Filed 10/17/24 Page 11 of 24 PageID #: 1427
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US 10 , 370 , 132 B2 

STRAPPING DEVICE HAVING A Furthermore , such strapping devices are configured to join 

PIVOTABLE ROCKER together only weldable plastic straps . For mobile devices , a low weight is of special importance , 

PRIORITY CLAIM in order to physically burden the user of the strapping device 

5 as little as possible when using the device . Likewise , for 

This application is a divisional application of . claims ergonomic reasons , the weight should be distributed as 

priority to and the benefit of U . S . patent application Ser . No . uniformly as possible over the entire strapping device , 14 / 430 , 163 , filed on Mar . 20 , 2015 as a 371 ( c ) Application especially in order to avoid a concentration of weight in the 

of PCT / IB2013 / 002116 , filed on Sep . 24 , 2013 , which head region of the strapping device . Such a concentration 

claims priority to and the benefit of Switzerland Patent nt 10 results in difficult handling of the device . Furthermore , the 

Application No . 1723 / 12 , filed on Sep . 24 , 2012 , and Swit most ergonomical and user - friendly handling of the strap ping device is always desired . In particular , the possibility of zerland Patent Application No . 1724 / 12 , filed on Sep . 24 , wrong operation and malfunction should be kept as low as 2012 , the entire contents of each of which are incorporated possible . herein by reference . In strapping devices of this kind , moreover , it should be The present disclosure concerns a strapping device , such ensured as a further aspect of functional safety that even 

as a mobile strapping device , for strapping packaged goods after achieving rather high strap tensions little or no slip by way of a strap , which has a tensioning apparatus for occurs between the tensioning wheel and the strap . Slip , on applying a strap tension to a loop of a strap , wherein the the one hand , can prevent the achieving of the possible strap tensioning apparatus is provided with a tensioning wheel 20 tension values . But slip can also cause a longer time for the 

which can be rotationally driven about a tensioning axis in tensioning process and thus the overall strapping process . a motorized manner , being configured to engage with the Moreover , due to the longer time of use of the particular 

strap , the tensioning apparatus furthermore having a ten - strapping device per strapping operation and thus also the 

sioning plate , wherein it is provided during a strapping amount of energy needed per strapping operation , slip can 

process performed by the tensioning apparatus that a one or 25 also reduce the number of strapping operations for a single 

two - ply segment of strap is located between the tensioning charge of the storage battery . Finally , slip also means that the 

wheel and the tensioning plate and makes contact with both desired strap tension value might not be achieved and thus 

the tensioning wheel and the tensioning plate , and moreover the strap is not sufficiently taut , which can constitute a safety 

the tensioning wheel and / or the tensioning plate is arranged risk . In order to avoid slip as much as possible or at least 

on a rocker which can pivot in a motorized manner about a 30 reduce it , the tensioning wheel is usually provided with teeth 

rocker axis in order to either increase or decrease a distance and pressed by a force against the tensioning plate . The 

between the tensioning wheel and the tensioning plate by pressing force for this in known solutions can result from a 

way of a pivoting motion , as well as a connecting device to spring by which the rocker with the tensioning wheel 

produce a permanent connection , especially a welded con - arranged on it is pressed against the strap and the tensioning nection , at two superimposed regions of the loop of strap by 35 plate located underneath . However , these solutions cannot 

way of a connecting element , such as a welded element , be satisfactory , especially when higher strap tensions need to 

which is provided for the local heating of the strap be generated , since ( as has been discovered ) slip cannot be 

Such strapping devices are used for the strapping of sufficiently reliably prevented in this way during the ten 

packaged goods by way of a plastic strap . For this , a loop of sioning process . the particular plastic strap is placed about the packaged 40 Therefore , the problem which the present disclosure is 

goods . As a rule , the plastic strap is pulled off from a supply supposed to solve is to create a mobile strapping device of 

roll . After the loop has been placed completely about the the mentioned kind with high functional safety , in which the 

packaged goods , the end region of the strap overlaps with a intended strap tensions can be applied to the strap in a save 

segment of the loop of strap . The strapping device is now manner with as little slip as is possible . placed at this two - ply region of the strap , the strap being 45 This problem is solved by the present disclosure in a 

clamped in the strapping device , a strap tension is applied to strapping device of the mentioned kind in that during the 

the loop of strap by way of the tensioning apparatus , and a transmission of the motorized driving motion to the tension 

closure is produced between the two layers of strap by ing wheel , preferably for as long as the tensioning wheel is 

frictional welding on the loop . In this process , pressure is engaging with the strap , by way of at least one transmitting 

applied to the strap with a frictional shoe oscillating in the 50 device of the strapping device , a driving motion is trans 

region of the two ends of the loop of strap . The pressure and mitted to the rocker , which can be pivoted at least sometime 

the heat created by the motion melt the generally plastic during the course of the tensioning process , wherein the 

strap locally within a short time . This produces a lasting driving motion is intended to apply a torque to the rocker . connection between the two layers of strap , one which can According to the present disclosure , the torque applied to the 

only be loosened with great force . After this , or roughly at 55 rocker can be used to increase the pressing force of the 

the same time , the loop is separated from the supply roll . The tensioning apparatus against the strap . In one simple - design particular packaged goods have now been strapped . solution , the torque exerted on the rocker by transmitting 

Such strapping devices are intended for mobile use , device can come from a motor , whose driving moment 

during which the device is taken by the user to the particular increases the pressing force of the rocker against the strap in 

place of use , where one should not be dependent on the use 60 the course of the tensioning process . It is preferable for the 

of energy supplied from the outside . The energy required for motorized increasing of torque to occur especially during or 

the intended use of such strapping devices in order to tension after an increasing of the strap tension 

a strap about any given packaged goods and produce a Advantageously , a motor is used for the generating of the 

closure is generally provided by an electric storage battery motorized torque for the rocker that also performs other 

or by pressurized air in the case of known strapping devices . 65 driving motions . Especially favorably , one utilizes the motor 

This energy produces the strap tension applied by way of the and its driving motion with which the tensioning wheel is 

tensioning apparatus to the strap and a closure on the strap . also driven . On the one hand , this can make an additional 

Case 2:24-cv-00080-JRG Document 57-9 Filed 10/17/24 Page 15 of 24 PageID #: 1431
US 10 , 370 , 132 B2 

motor unnecessary , while still performing the function the reaction of the strap to the action , namely , the strap according to the present disclosure . On the other hand , the tension introduced , as well as transmitting devices are used 

motor torque which usually also increases with increasing for this , which are derived from the tensioning apparatus , strap tension can be utilized to increase the pressing force . especially the tensioning wheel , and transmitted to the 

This enables an especially simple design for variable press - 5 rocker , no intervention by the user is needed to achieve the 

ing of the rocker against the strap , independent of the action of the present disclosure , which is advantageously tension . The latter can be done proportionately to the par - accomplished automatically in the strapping device . ticular existing strap tension . In one embodiment of the present disclosure , the trans 

According to another aspect of the present disclosure , mitting device , which advantageously constitute an opera which is also of independent significance , a torque can also 10 tive connection between the tensioning wheel and the 

be applied to the rocker and transmitted that is based on a rocker , comprise a pivoting mounting of the rocker at least 

force exerted on the tensioning apparatus by the strap at a during the tensioning process and a rotary or rotationally 

point of engagement of the strap with the tensioning appa - mounted gearing element , which stands in an operative 

ratus . This force , which is a reaction of the tensioning force connection with the tensioning wheel during the tensioning applied by the driven tensioning wheel to the strap , can be 15 process . The force of reaction of the strap is utilized as a 

tapped from a suitable place and be transmitted to the rocker torque and transferred to the rotary or rotational gearing by transmitting device . For the least possible structural element , such as a planet carrier of a planetary gearing . The 

expense , the strap tension force at the tensioning wheel itself rotary or rotational gearing element should be propped which is acting on the tensioning wheel can also be utilized against a support element to resist the turning or rotating 

In particular , this can be used as torque acting on the 20 movement . The force of reaction of the tensioning wheel can 

tensioning wheel at any given time , which is taken from the then be transferred to the rocker through or by virtue of the 

tensioning wheel to the transmitting device of the tensioning support , so that an additional torque will act on the rocker , apparatus and transmitted by them to the rocker . which can be utilized to increase the pressing force of the 

Thus , according to the present disclosure , it is provided in rocker against the strap . The transmitting device can advan 

advantageous fashion that the motorized driving movement 25 tageously be part of or the entire tensioning gearing by 

for the tensioning apparatus is also used at least indirectly as which a motorized driving movement or one coming from 

a reaction , making use of the rotational movement driven by another energy supply source is directed with suitable rota 

the motor of the tensioning wheel as well as a pivoting tional speed toward the tensioning wheel . capability of the rocker during the tensioning process , to In an embodiment of the present disclosure , which also 

transfer a torque tapped by the tensioning wheel in engage - 30 has independent significance , motorized driving movements 

ment with the strap by way of the transmitting device to the can be utilized with identical directions of rotation of the 

rocker in order to increase a pressing force of the tensioning only one motor not only to drive the tensioning wheel during apparatus against the strap . the tensioning of the strap but also for a lifting of the rocker . In one embodiment of the present disclosure , a gearing of In addition to this , the same driving movement can also be 

the tensioning apparatus by which a motorized driving 35 used for the variable pressing of the tensioning wheel 

movement for the tensioning wheel can be stepped up or against the strap being tensioned , in dependence on the strap down , can be part of or the entire transmitting device with tension . The dependency is organized in this case such that , which the force acting on the tensioning wheel and resulting with increasing strap tension , the pressing force exerted by 

from the strap tension is transmitted from the strap to the the tensioning wheel on the strap also increases . Since with 

rocker . 40 increasing strap tension the danger also increases of a 

According to another aspect , the present disclosure can slippage occurring between the tensioning wheel and the 

also be seen in that devices are provided for the variable strap , one can counteract the danger of slippage by providing 

pressing of the tensioning wheel or the tensioning plate an increasing pressing force . In this embodiment the same 

against the strap , depending on the strap tension . Thus , the direction of turning of the motor as for the tensioning is 

present disclosure calls for a variable pressing of the ten - 45 used . The motorized driving movement during the tension 

sioning apparatus against the strap , depending on the strap ing of the strap can be utilized such that , during the 

tension . tensioning process of the strap by way of the tensioning 

In especially advantageous embodiments of the present wheel engaging with the strap and rotating against a strap disclosure , the strap tension created by the tensioning pro - tension , a counterforce acting from the strap to the tension 

cess is thus used advantageously to increase as well the 50 ing wheel is utilized to increase the pressing force of the 

pressing force of the tensioning wheel and / or the tensioning tensioning wheel in the direction of the tensioning plate . plate on the strap as the strap tension increases steadily , According to another aspect of the present disclosure , it 

thereby working against the constantly increasing danger , as should be made possible with little design expense and easy 

the strap tension likewise increases , of a “ slip - through ” or operating capacity to maintain and release a force resulting slippage of the tensioning wheel during the tensioning 55 from the strap tension and operating reactively on a gearing 

process . Thus , as the strap tension increases , so too does the in order to transfer a driving movement to the tensioning pressing force of the tensioning wheel against the strap and wheel . The present disclosure thus concerns a locking device 

the tensioning plate . The present disclosure in such embodi for use in a strapping device , with which a rotatable wheel 

ments thus makes it possible to exert a high pressing force can be clamped , which is provided for transmission of a 

on the strap when the strap tension is already high and thus 60 driving movement , especially a gearing wheel of a tension 

the danger of slippage between the tensioning wheel and the ing apparatus of the strapping device . The locking device 

strap is likewise especially high if it is attempted to further according to the present disclosure should have at least one 

increase the strap tension . Thanks to the likewise increasing clamping body which can pivot about an axis and is arranged 

pressing force in automated manner , i . e . , without manual at a distance from the wheel , which can be pivoted from a 

intervention , one can counteract the increasing danger of 65 release position into a locking position in which it bears by slippage and thus ensure the functional safety as well as a a portion of an arc - shaped contact surface against an essen 

rapid strapping process even with high strap tension . Since tially planar peripheral clamping surface of the wheel , i . e . , 

Why 

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US 10 , 370 , 132 B2 

one which is free of form - fitting elements , wherein the FIG . 9 a side view of the tensioning apparatus of FIG . 5 , clamping body has a pivot radius which is greater than a in which the rocker is located in a second pivot end position ; 

distance from the pivot axis of the clamping body to the FIG . 10 a side view of the tensioning apparatus of FIG . 2 , peripheral clamping surface of the wheel , and the rotating of in which the rocker is located in a position with large 

the clamping body about the pivot axis during the movement 5 pressing force against a tensioning plate ; 

from the release position to a clamping position occurs in the FIG . 11 a side view of the tensioning apparatus of FIG . 2 , opposite direction of turning to that of the wheel being in which the rocker is located in a position with less pressing 

clamped . force against a tensioning plate as compared to FIG . 10 ; 

FIG . 12 a partial perspective representation of the ten With such a locking device , one can accomplish very functionally secure locking of rotating gear wheels in a 10 sioning and closure mechanism ; 

FIG . 13 a sectional representation of the tensioning and simple designed manner . The locking in the direction of closure mechanism ; turning of the wheel can be maintained with little force FIG . 14 a schematic diagram of the geometrical relations expenditure . The clamping force of the clamping body even of a strapping device . increases automatically if one should try to turn the wheel 15 The strapping device 1 shown in FIGS . 1 and 2 . being further by increasing the torque . exclusively manually operated , has a housing 2 , which The locking mechanism according to the present disclo encloses the mechanism of the strapping device and on 

sure can be used with advantage especially for the releasable which a handle 3 is fashioned for handling the device . The 

locking of a wheel of a gearing which belongs to a gearing strapping device , moreover , is provided with a base plate 4 , by which a driving movement is supposed to be transmitted 20 whose bottom side is provided for being placed on an object 

to a tensioning wheel of the tensioning apparatus of a being packaged . All the functional units of the strapping 

strapping device . In this context , it can be provided espe - device 1 are fastened to the base plate 4 and to the carrier 

cially for the clamping of a wheel of a planetary gearing by connected to the base plate , not otherwise depicted . which the driving movement is to be transmitted to the With the strapping device 1 , one can tension a loop of 

tensioning wheel . With or at least assisted by a clamping of 25 plastic strap B , not otherwise shown in FIG . 1 , for example , 

the wheel being clamped , one can define one of at least two one made of polypropylene ( PP ) or polyester ( PET ) , which 

takeoff directions of the gearing , in particular a takeoff has previously been placed around the object being pack direction of the gearing toward the tensioning wheel , so that aged , by way of a tensioning apparatus 6 of the strapping 

the strap can be tensioned . device . For this , the tensioning apparatus has a tensioning 

Moreover , it can be advantageous with a loosening of the 30 wheel 7 , with which the strap B can be grasped for a 

clamping to also remove at least partly , or entirely , the strap tensioning process . The tensioning wheel 7 is arranged on a 

tension acting on the tensioning wheel and the gearing . pivoting rocker 8 , which can swivel about a rocker pivot axis 

Since with such locking mechanisms relatively low release 8a . The tensioning wheel 7 , arranged with its axis of rotation 

forces are needed to remove the clamping , even for high at a distance from the rocker pivot axis 8a , can be moved by 

strap tension values , the present disclosure produces espe - 35 a pivoting motion of the rocker 8 about the rocker pivot axis 

cially functionally safe and easy to operate strapping 8a from one end position with a distance from a curved 

devices . The low operating and activating forces make it tensioning plate 9 arranged on the base plate 4 to a second 

possible to do without a rocker handle , with which large end position in which the tensioning wheel 7 is pressed 

torques have been produced heretofore in known strapping against the tensioning plate 9 . By a corresponding motor 

devices for lifting the rocker from the taut strap . Instead of 40 driven movement in the reverse direction of rotation about 

a long rocker handle , one can now use a button or switch the rocker pivot axis 8a , the tensioning wheel 7 can be 

with which the tension releasing process occurs . removed from the tensioning plate 9 and swiveled back to its 

Other embodiments of the present disclosure will emerge starting position , such that the strap located between the 

from the claims , the specification , and the drawing . tensioning wheel 7 and the tensioning plate 9 is released for 

The present disclosure shall be explained more closely 45 removal . with the help of sample embodiments represented schemati - During use of the indicated embodiment of tensioning 

cally in the figures . There are shown : device , two layers of the strap are situated between the 

FIG . 1 a strapping device according to the present dis tensioning wheel 7 and the tensioning plate and are pressed 

closure in a perspective representation ; by the tensioning wheel 7 against the tensioning plate . By 

FIG . 2 an exploded representation of the tensioning 50 rotation of the tensioning wheel 7 , it is then possible to 

apparatus of the strapping device from FIG . 1 with the provide a sufficiently large strap tension to the strap loop for 

motor ; packaging purposes . The tensioning process and the ten 

FIG . 3 a perspective representation of the tensioning and sioning device and rocker 8 advantageously designed for 

closure mechanism of the strapping device from FIG . 1 ; this shall be explained more closely below 

FIG . 4 another perspective representation of the tension - 55 After this , a welding of the two layers can be done in 

ing and closure mechanism of the strapping device from familiar fashion at a location of the strap where the two 

FIG . 1 ; layers of the strap loop are superimposed on each other , by 

FIG . 5 an exploded representation of another sample way of the friction welding device 12 of the strapping embodiment of the tensioning apparatus of the strapping device . In this way , the strap loop can be permanently device from FIG . 1 together with the motor ; 60 closed . In the sample embodiment shown here , the friction 

FIG . 6 a perspective representation of the tensioning and welding and separating mechanism 12 is actuated by the 

closure mechanism of the strapping device from FIG . 1 ; same only one motor M of the strapping device with which 

FIG . 7 another perspective representation of the tension - all other motor - driven movements are also performed . For 

ing and closure mechanism of the strapping device from this , in familiar manner , there is provided a not otherwise 

FIG . 1 ; 65 depicted freewheeling in the direction of transmission from 

FIG . 8 a side view of the tensioning apparatus from FIG . the motor M to the places where the motorized driving 

5 , in which a rocker is located in a first pivot end position ; movement occurs , which has the effect that the driving 

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US 10 , 370 , 132 B2 

movement is transmitted in the particular desired rotary pressed against two overlapping layers of the strap can be 

driving direction to the corresponding functional unit of the placed in an oscillatory movement with predetermined fre 

strapping device and no transmission occurs in the other quency and amplitude , by which the two strap layers are 

particular rotary driving direction of the motor . locally melted in the region of the welding shoe and welded 

The friction welding device 12 for this is provided with a 5 together by the subsequent cool down . welding shoe 13 , shown only highly schematized , which is On the drive shaft of the motor , situated behind the 

moved by way of a transmission mechanism 14 from a toothed belt drive for the welding mechanism as seen from 

position of rest at a distance from the strap to a welding the motor M , there is a bevel gear 19 , which belongs to a 

position in which the welding shoe is pressed against the bevel gearing of the tensioning apparatus , as does a second 

strap . The welding shoe pressed by mechanical pressure 10 bevel gear 20 meshing with it . On the same shaft where the 

against the strap in this way and the simultaneously occur - second bevel gear 20 is arranged there is also located a first 

ring oscillating movement of the welding shoe with a gear 21 of another toothed belt drive 22 , which is further 

predetermined frequency melts the two layers of the strap . more led across a second gear 23 . The first gear 21 of the 

The locally plasticized or melted regions of the strap B flow toothed belt drive 22 is arranged on the shaft 24 firmly 

into one another and after a cooldown of the strap B there is 15 against rotation . produced a connection between the two strap layers . Insofar On the other end of the shaft 24 is mounted the rocker 8 

as is necessary , the strap loop can then be separated from the of the strapping device , being part of the tensioning appa supply roll of strap by way of a cutting device of the ratus 6 and also carrying an upstream gearing from the 

strapping devices 1 , not otherwise depicted . tensioning wheel 7 , in the present case a planetary gearing The infeed of the tensioning wheel 7 in the direction of the 2026 , for which suitable bearing sites can be provided on the 

tensioning plate 9 , the rotary driving of the tensioning wheel rocker 8 . The rocker 8 is shoved onto the shaft 24 such that 

7 about the tensioning axis 6a , the lifting of the tensioning the rocker 8 is arranged and supported so that the rocker 8 

wheel from the tensioning plate , the infeed of the friction can pivot about the longitudinal axis of the shaft 8 . The 

welding device 12 by way of the transmission mechanism 14 longitudinal axis of the shaft 24 is thus at the same time the 

of the friction welding device 12 as well as the use of the 25 rocker pivot axis 8a , about which the rocker 8 can swivel . friction welding device 12 in itself and the activating of the The planetary gearing 26 can be configured as a single or 

cutting device occur by use of only a single common electric multiple - stage planetary gearing , in particular , a two or 

motor M , which provides each time a driving movement for three - stage planetary gearing . From an end face of the gear 

these components of the strapping device . For the power 23 facing the tensioning wheel 7 , there sticks out an exter 

supply of the motor M , a replaceable storage battery 15 is 30 nally toothed input sun gear 30 belonging to the planetary 

arranged on the strapping device , especially one which can gearing 26 , whose axis of rotation is identical to the axis of 

be removed for recharging , which serves to store up elec - rotation ba of the input gear 23 . On a shaft of the gear 23 on trical energy . A supply of other external auxiliary energy which the sun gear 30 is also configured in the sample such as pressurized air or other electricity can be provided embodiment , a freewheeling 45 is provided , which only but does not occur in the case of the strapping device per 35 enables one rotary direction of the sun gears 30 , namely , the 

FIGS . 1 and 2 . rotary direction which is provided for the driving of the 

As shown in FIG . 4 , the strapping device according to the tensioning wheel . The sun gear 30 is led through a ring gear 

present disclosure provides for a tapping of the driving 27 and through a central recess of a planet carrier 25 , which 

movement of the motor M at two places of its drive axis , are likewise part of the planetary gearing 26 . Looking from 

either for the tensioning apparatus 6 or for the friction 40 the input side of the planet gear , the planet carrier 25 is 

welding device 12 . For this , the motor M can be operated in arranged behind the ring gear 27 on the axle of the planetary either of the two rotary directions . The shifting of the gearing 26 corresponding to the tensioning axis 6a . The 

transmission of the driving movement to the tensioning planet carrier could also be configured as a clamping , apparatus 6 or to the friction welding device 12 is done coupling or spur gear . automatically by a freewheeling arranged on the drive shaft 45 The ring gear 27 has at its outer circumference a cam 27c , of the motor M ( and not otherwise shown ) independence on which engages with an abutment 46 secured to the base plate 

the rotary direction of the drive shaft of the motor . In one 4 of the strapping device . The internally toothed ring gear 27 

rotary direction of the drive shaft , the driving movement is is supported in this way so that the cam 27c can execute 

transmitted to the tensioning apparatus 6 . Thanks to the slight relative movements within its engagement with the 

freewheeling , the friction welding device 12 experiences no 50 abutment 46 , for example , in a recess 46a of the abutment . driving movement in this case . In the other rotary direction , Furthermore , the ring gear 27 has a ring - shaped shoulder 

the tensioning apparatus 6 has no driving movement and the 27a , on which a roller bearing 28 is arranged for the 

friction welding device 12 is driven . No manual shifting is mounting of the planetary gearing 26 . required in this embodiment for changing the direction of The planet carrier 25 , whose axis is aligned with the 

transmission of the motorized driving movement . Such 55 tensioning axis 6a , engages by its three planet gears 25b 

freewheeling in connection with a strapping device is with an internal toothing of the input ring gear 27 of the 

already known , and so it shall not be further discussed here . planetary gearing 26 . The planet gears 25b of the planet 

As is likewise shown in FIG . 4 , the motorized transmis carrier 25 furthermore engage with the sun gear 30 , from 

sion of the driving movement to the friction welding device which they can obtain a driving movement and transmit it , 12 and transmission mechanism 14 occurs by any suitable 60 appropriately stepped down , to the ring gear 27 . Thus , given 

manner . This might be , for example , a toothed belt drive a rotationally fixed arrangement of the planet carrier 25 , a 

with a toothed belt closed into a ring . One of the two gears rotational movement of the sun gear 30 can be converted 

is arranged on the drive shaft of the electric motor M , the into a rotational movement of the ring gear 27 . In the sample other one belongs to a gearing of the friction welding device embodiment , a first clamp 29 of a locking mechanism is 

12 , by which the motorized driving movement moves both 65 configured as a pivoting cam , which can be brought into 

the transmission mechanism 14 and the welding shoe 13 of contact with a clamping surface 25a on the outer circum 

the friction welding device 12 . In this way , the welding shoe ference of the planet carrier 25 or pivoted away from the 

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US 10 , 370 , 132 B2 

10 

clamping surface 25a with a spacing . The cam is arranged so with a fine toothing on its external circumferential surface , that , upon contact of the cam with the clamping surface 25a is utilized to grasp the strap B with the circumferential 

by a rotation of the input planet carrier 25 in the rotary surface and pull back the strap of the strap loop , thereby direction provided for the planet carrier 25 , the clamping increasing a strap tension in the strap loop . action is further intensified . By an infeeding of the cam onto 5 The third planet carrier 37 has a shoulder 37a on its outer the clamping surface 25a by a corresponding shifting move surface , which can be brought into contact against a stop ment , the planet carrier 25 can be blocked against rotation . element 39 by a rotational movement . The stop element 39 By another shifting movement , the cam 29 can be moved itself is fixed not to the rocker , but to the base plate 4 or some away from the clamping surface 25a , thereby releasing the other carrier , which does not participate in the pivoting planet carrier 25 for rotational movements . The shifting 10 ' motion of the rocker 8 . Thus , the stop element 39 is movement can trigger a pivoting motion of the clamp 29 stationary in regard to the shoulder 37a . about a shift axis 143 , which is produced by activating a 

button 44 . In use when strapping packaged goods , the strapping 

The sun gear 30 is furthermore arranged in the region of of device 1 behaves as follows : after a loop of a customary 

the axis of rotation 31 of a ring gear 32 , whose nontoothed 15 Plastic strap has been placed around the particular packaged 

external surface 32a is coordinated with a second clamp 33 . goods , this is placed inside the strapping device in the region 

The axis of rotation 31 is identical to or aligned with the of the end of the strap where the strap loop is double - ply for 

tensioning axis ba . The clamp 33 interacting with the outer a certain length , and the end of the strap is secured in the 

surface 32a can essentially be configured in the same way as strapping device by a strap clamp , not otherwise depicted . A 

the first clamp 29 as a shifting cam , which can move 20 section of the strap B immediately next to the strap loop is 

between two end positions , whereby in the one position the placed in double layer on top of the tensioning plate 9 of the 

ring gear 32 is blocked against rotation and in the other tensioning apparatus 6 . The rocker 8 with the tensioning position the ring gear 32 is released for rotational move wheel 7 and the upstream gearing 26 is situated in its upper 

ments . Moreover , an internal toothing of the ring gear 32 end position , in which the tensioning wheel 7 is arranged at 

engages with three planet gears 34 , which are mounted at the 25 a spacing ( by its greatest design spacing ) from the tension 

end face of the following planet carrier 35 , facing the ring ing plate 9 , so that the largest possible opening gap is 

gear 32 . The planet gears 34 of the planet carrier 35 produced , enabling an easy , comfortable and thus also rapid 

furthermore engage with the sun gear 30 of the input gear 23 , placement of the strap in the tensioning apparatus . After this , which protrudes into the ring gear 32 . the rocker is lowered onto a tensioning plate 9 opposite the 

The locking device in the embodiment being described is 30 tensioning wheel 7 and pressed against the strap arranged configured so that always only one of the gears 25 , 32 is between the tensioning plate 9 and the tensioning wheel 7 . clamped against rotation and the other gear 25 , 32 is free for Both this transfer movement of the tensioning wheel and the 

rotational movements . Thus , depending on the positions of magnitude of the pressing force exerted on the strap by the 

the locking devices 29 , 33 , it is possible for a rotational tensioning wheel at the start of the tensioning process can be 

movement of the gear 23 and the sun gear 30 to result in 35 produced in the described embodiment of the present dis 

either a rotation of the planet carrier 35 about the tensioning closure by one or more prestressed spring elements 44 ( not 

axis ba and axis of rotation 31 by virtue of a movement of shown ) . By activating a button 10 , the spring element can be 

the planet gears 34 in the internal toothing of the ring gear released and the entire strapping process triggered with its 

32 . Or the rotation of the sun gear 30 depending on the consecutive steps of “ tensioning " , " closing " , " cutting ” , positions of the locking device results in a rotation of the 40 releasing the tension of the strap in the region of the 

ring gear 32 . If the planet carrier 25 is not clamped by the tensioning apparatus , and “ lifting of the rocker ” , for which 

locking mechanism , the rotating sun gear entrains the planet no further intervention by the user of the strapping device 

gears 25b so that the planet carrier 25 rotates and the ring need occur . gear 27 remains stationary . On the other hand , if the ring After the tensioning wheel 7 is moved automatically from 

gear 32 is not clamped , a rotation of the sun gear 30 results 45 the open position to its tensioning position ( see the tension 

in an entrainment of the planet gears 34 , which in turn set the ing position in FIG . 10 and the open position in FIG . 11 ) , ring gear 32 in a rotational movement . Since the resistance where the tensioning wheel 7 lies on the strap B and presses 

to rotation in the further course of the planetary gearing 26 across the strap on the tensioning plate 9 , the motorized 

is greater toward the tensioning wheel 7 than the torque driving movement is transmitted to the tensioning wheel 7 . needing to be overcome in order to set the ring gear 32 in 50 Now the second clamp 33 is moved into its position in which 

rotation , the ring gear 32 will primarily rotate in this case the second clamp 33 presses against the ring gear 32 . The 

and the tensioning wheel 7 at least for the most part will not ring gear 32 is thereby arrested from rotational movements 

rotate . and locked . The first clamp 29 , on the other hand , continues 

At the other end face of the planet carrier 35 , turned to be positioned at a spacing from the input planet carrier 25 

toward the tensioning wheel 7 , there is arranged rotationally 55 and releases the ring gear 27 for rotational movements . The 

firm on the planet carrier 35 another sun gear 36 , which motorized driving movement , which thanks to the particular 

meshes with planet gears 41 of another planet carrier 42 . A designated rotary direction of the motor M is transmitted via 

further sun gear 43 directed toward the tensioning wheel 7 the bevel gearing 19 , 20 , 21 to the second toothed belt drive 

and connected rotationally firm to the planet carrier 42 is led 22 and thus to the gear 23 , goes from here in the sequence 

through a recess of the additional planet carrier 37 , config - 60 of the following mentioned gearing elements via the input 

ured as a ring gear . The sun gear 43 stands in meshing gear 23 , the sun gear 30 , the planet gears 34 , the sun gear 36 , engagement with planet gears 38 of the additional planet the planet gears 41 , the sun gear 43 and via the planet gears carrier 37 , facing the tensioning wheel 7 The planet gears 38 38 to the tensioning wheel 7 . The tensioning wheel 7 can be 

of the second planet carrier 37 mesh in turn with an internal driven by the multistage planetary gearing in greatly toothing of the tensioning wheel 7 and drive the latter in its 65 stepped - down rotational movement of the motor and thus 

rotational movement about the tensioning axis 6a . This when necessary with correspondingly high torque in the 

rotational movement of the tensioning wheel 7 , provided predetermined rotary direction . 

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US 10 , 370 , 132 B2 

12 

In the just described “ tensioning ” operating state of the force acting from the tensioning wheel 7 on the strap B , with 

strapping device , the driven tensioning wheel 7 in engage - which the strap B is pressed by the tensioning wheel 7 

ment with the strap produces a corresponding , oppositely against the tensioning plate 9 . Therefore , in the present 

directed counterforce on the tensioning wheel 7 , depending disclosure , an increasing strap tension from the motorized 

on the resistance resulting from the strap tension and acting 5 driving movement on the tensioning wheel 7 goes hand in 

on the tensioning wheel 7 . This counterforce acts in the hand with an increasing pressing force of the tensioning 

reverse direction of transmission of the motorized driving apparatus on the strap . movement on all gearing elements of the multistage plan - After the ending of the tensioning process and the fol 

etary gearing that are involved in the transmission of the lowing welding process to form the closure and also after a 

driving movement . If a different type of gearing from a 10 motorized driven cutting process by a cutting device , not 

single or multiple - stage planetary gearing is used , the coun - otherwise depicted , integrated in the strapping device , a 

terforce resulting from the already applied strap tension and quick and uncomplicated removal of the strap from the 

put into the respective gearing via the contact with the strapping device should be possible . To accomplish this , tensioning wheel is also available for use in accordance with there is provided a motorized lifting movement of the 

the present disclosure . According to the present disclosure , 15 tensioning wheel 7 from the clamping position . For this , the 

this counterforce can be used to improve the conditions of button is activated and for as long as the button 10 is 

the process , especially the functional safety even when the activated the rocker also remains in the open position , in 

applied strap tension is high . Thus , in order to use this which a sufficient spacing is created between the tensioning 

counterforce for the following described purpose , it would plate 9 and the tensioning wheel 7 . By releasing the button 

be possible in theory to use each of these gear elements for 20 10 , the rocker is closed , for example , by spring force . this , in particular , to pick off and employ the mentioned In the sample embodiment , to accomplish this at first the 

counterforce at each of these gear elements . operative connection between the electric motor M and the 

In the sample embodiment , the planet carrier 37 is used tensioning wheel 7 is released and an operative connection 

for this . The planet carrier 37 is buttressed in this case via the is created between the electric motor M and the rocker 8 . stop element 39 against the base plate 4 , so that the entire 25 This is accomplished by switching the clamps 29 , 33 . The 

tensioning apparatus 6 is pressed about the rocker axis 8a previously existing clamping of the ring gear 32 is lifted in 

against the strap in proportion to the force of resistance that the second clamp 33 is removed from the outer surface 

( strap tension ) . The tensioning wheel 7 is thus pressed 32a of the ring gear 32 and in this way the ring gear 32 is 

against the strap B proportionally to the strap tension . The released for rotational movements . Basically at the same 

strap tension generated by the tensioning process is utilized 30 time or shortly thereafter , the first clamp 29 is lowered onto 

in advantageous manner to increase the pressing force of the the clamping surface 25a of the planet carrier 25 and brought tensioning wheel 7 on the strap B as the strap tension to bear against it in clamping fashion . In this way , the input increases steadily , so that the danger of a “ slip - through ” or planet carrier 25 is fixed and locked against a rotational 

a slippage of the tensioning wheel 7 during the tensioning movement about the tensioning axis 6a , along which the 

process , which also increases with increasing strap tension , 35 entire planetary gearing is situated . 

can be counteracted In this way , the tensioning wheel 7 can turn freely without 

For this , the planet carrier is configured with the engaging being driven and no longer has an operative connection to 

element 37a , which interacts with the stationary stop ele - the electric motor M or the sun gear 30 , such as might 

ment 39 . The engaging element , configured as a cam and transmit a driving movement . A driving movement of the 

arranged on the outer circumference of the planet carrier and 40 electric motor M with the same rotary direction as during the 

projecting essentially radially from it , is buttressed against tensioning process is now utilized , thanks to the locking of 

the stop element 39 . As can be seen from FIG . 3 , for this the input planet carrier 25 of the planetary gearing , so that 

purpose the stationary stop element 39 is located in the the planet gears 25b of the spur gear 25 entrain the input ring 

region of the head end of the strapping devices . The stop gear 27 in their rotational movement . The input ring gear 27 

element 39 in the sample embodiment shown is situated on 45 thus executes a rotational movement by virtue of the rotating 

one side , namely , the head end , of the tensioning axis 6a and planet gears 256 . The bearing and abutment of the ring gear 

the rocker pivot axis 8a running essentially parallel to it is 27 on the abutment element 46 leads to a pivoting motion of 

on the other side of the tensioning axis 6a . The rocker 8 , on the ring gear 27 about the rocker axis 8a . The input ring gear which the planet carrier 37 is arranged via a roller bearing 27 , which is also connected rotationally firm to the rocker 8 

and able to rotate about the tensioning axis ba , is also able 50 thanks to the clamping , entrains the rocker 8 during this 

to swivel at least during the tensioning process , i . e . , it is not movement . This results in a lifting of the rocker 8 and the 

blocked against pivoting motions but instead released for tensioning apparatus 6 secured to it , including the tensioning 

these . Furthermore , the planet carrier 37 is able to rotate wheel 7 . The rotational movement of the rocker 8 can be 

during the tensioning process about the tensioning axis 6a . limited by an end stop or an end position sensor , which shuts 

The strap tension created in the strap B as a reaction to the 55 off the motor M after reaching an end position in the opened tensioning process brings about a force on the tensioning position of the rocker 8 and triggers an arresting of the 

wheel 7 which is opposite the rotary direction of the ten - rocker . Thanks to the motorized lifting movement of the 

sioning wheel provided during the tensioning process . This rocker 8 against the direction of action of the spring element 

reaction force acts from the tensioning wheel via the planet 44 , the spring element 44 also is once more provided with 

carrier 37 on the rocker 8 as a torque directed about the 60 a greater prestressing force . The strap B can now be removed 

rocker pivot axis 8a , by which the planet carrier 37 is from the strapping device 1 . pressed with increased force against the strap in the direction The strapping device is now ready for a new strapping of the tensioning plate 9 . The higher the strap tension already process , which can occur in the same way as the previously 

produced in the strap , the higher the torque resulting from described strapping process . In order to lower the rocker 8 

this and from the motorized driving movement continuing to 65 after introducing a new piece of strap B in the strapping 

act on the tensioning wheel 7 . This torque , arising as a device 1 , the spring element 44 must be released again , reaction , is in turn proportional to the resulting pressing which can be done for example via an operator button on the 

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US 10 , 370 , 132 B2 

13 

strapping device . In the sample embodiment , the previously 105b of the planet carrier 105 . The internal toothing of the 

actuated button 10 is released for this . The spring force then ring gear 109 which engages with these planet gears 1056 

swivels the rocker , now in the opposite direction , against the places the latter in rotational movement . As is especially tensioning plate and clamps the strap for the next tensioning seen in FIG . 7 , an external toothing 109c of the ring gear 109 

process with an initial pressing force between the tensioning 5 engages with an external toothing 150c of a circular arc 

wheel 7 and the tensioning plate 9 . The variable pressing segment 150 , which is disposed stationary on one end of a 

force in the rest of the tensioning process increases in the connection shaft 151 . The connection axis 151a of the 

manner described . connection shaft 151 runs parallel to the stationary tension 

In FIG . 5 to 9 is shown another sample embodiment of a ing axis 86a of this sample embodiment . Instead of the two 

strapping device according to the present disclosure . In 10 external toothings 109c , 150c , the ring gear 109 could also 

regard to its external appearance , this can also correspond to be braced by a cam against an abutment element , in which 

the representation of FIG . 1 . The basic layout of this case either the cam or the abutment element is neither 

embodiment of the strapping device can also correspond to fastened to the ring gear 109 nor movable in design and the 

that of the previously discussed embodiment of the present other of the two elements should be disposed on the ring disclosure . Accordingly , in this embodiment as well , only a 15 gear 109 . single motor M is used , which is provided to drive the The rotational movement of the ring gear 109 and the 

welding mechanism 12 and separating mechanism ( not engagement of the ring gear 109 with the circular arc 

shown in FIG . 5 ) in one of the two directions of rotation of segment 150 results in a rotational movement of the con 

the motor on the one hand and the tensioning apparatus 6 on n ection shaft 151 about the connection axis 151a . A spur 

the other hand in the other direction of rotation of the motor . 20 gear 152 arranged at the other end of the connection shaft 

The optional driving of either the welding mechanism and 151 engages with an external toothing 117c of the planet 

separating mechanism on the one hand or the tensioning carrier 117 and in this way transmits the rotational move 

apparatus 6 on the other hand is done via a freewheeling and ment about the connection axis 151a to the planet carrier 

different directions of rotation of the motor M . 117 . In relation to the tensioning axis 86a , the connection 

The embodiment likewise shows a pivoting rocker 80 of 25 axis 151a is situated on one side and the rocker pivot axis 

the tensioning apparatus 86 , driven by motor about a rocker 80a on the other side of the tensioning axis 86a , the rocker 

pivot axis 80a . In contrast with the previously explained pivot axis 80a being located on the side of the head end of 

sample embodiment , here it is not the tensioning wheel 87 the strapping device . but instead the tensioning plate 89 which is arranged on the The planet carrier 117 belongs to the drive train provided 

pivoting rocker 80 , whose rocker pivot axis 80a runs parallel 30 for the driving movement of the tensioning wheel 87 . The 

to the tensioning axis 86a . The motorized driving movement operative connection of this drive train to the motor M is 

with the direction of rotation which is used for rotational momentarily broken thanks to the above described shifting 

movements about the tensioning axis 86a is also used in this process of the locking mechanism . Thus , at the above 

sample embodiment for the pivoting motion of the rocker described moment in the process there is no operative 

80 . The rocker pivot axis 80a in this embodiment as well 35 connection of the motor M with the tensioning wheel 87 to 

runs essentially parallel to the tensioning axis 86a , about drive the latter . As a result of the rotary movement trans 

which the tensioning wheel can rotate . The rotational move - mitted to the planet carrier 117 , the planet carrier 117 rotates 

ment of the motor is transmitted , behind a point at which the about the tensioning axis 86a and entrains a dog 80c of the 

motorized driving movement is utilized for the welding rocker 80 by a cam 117a arranged on its outer circumfer 

mechanism , across a bevel gear pair 99 , 100 to a planetary 40 ential surface . As a result , the rocker 80 , appearing as an arc 

gearing 106 and from this it goes further to the tensioning in plan view , is rotated and opened . wheel 87 . A freewheeling 125 arranged on the shaft of an The rocker 80 , able to turn about the rocker axis 80a and input sun gear 110 ensures that the input side of the planetary having the approximate shape of an arc segment , is arranged gearing 106 can only turn in one rotary direction . The with its lower free end underneath the tensioning wheel 87 , planetary gearing 106 is provided with gear elements which 45 so that the tensioning plate 89 arranged in the region of the 

can be optionally arrested by way of a locking mechanism free end of the rocker 80 can likewise be arranged directly 

having two clamps 29 , 33 , as in the previously described beneath the tensioning wheel 87 . In order to arrange the 

sample embodiment , so that the driving movement can be tensioning plate 89 with a spacing from the tensioning wheel 

transmitted either to the tensioning wheel 87 or to the rocker 87 , the previously described motorized driven movement of 

80 . 50 the rocker 80 is used in the rotary direction along arrow 112 

In order to open the tensioning apparatus 86 , the ring gear ( FIG . 6 ) , by which the rocker 80 is opened as described and 

107 is released via the locking device , i . e . , the clamp 33 is a spacing between the tensioning wheel 87 and the tension 

not in clamping engagement with the ring gear 107 . The ing plate 89 is increased . The opening movement can be 

tensioning wheel 87 can in this way turn freely without an limited by an end stop . The motor - opened rocker 80 now 

operative connection with the motor M . Optionally , strap 55 enables a removal of the tensioned and closed packaging 

tension still acting on the tensioning wheel 87 from the strap strap from the strapping device . After the finished strapping 

B from the previous tensioning process is released in this is removed , the end of a new strapping loop for the next 

way by the tensioning wheel 87 and the gearing 106 tensioning process can be introduced between the tensioning 

upstream from the tensioning wheel . With the clamp 29 , the plate and the tensioning wheel . The rocker 80 can be brought 

spur gear configured as a planet carrier 105 is locked , and its 60 back once again to the tensioning wheel by the restoring 

axis of rotation is aligned with the tensioning axis 86a , i . e . , force of the spring element 124 previously stretched during 

the axis of rotation of the tensioning wheel 87 . The motor - the opening movement and press the strap against the 

ized driving movement transmitted from the bevel gear 100 tensioning wheel with an initial pressing force for the 

to the input sun gear 110 , thanks to the removable rotary tensioning process . In order to utilize the spring force and 

arresting of the planet carrier 105 performed by way of the 65 thereby move the rocker 80 in a rotary direction along arrow 

clamp 29 , does not lead to a rotation of the planet carriers 113 in the direction of the tensioning wheel 87 , an activation 

105 but instead to rotational movements of the planet gears of a button or some other activating element can be pro 

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vided , by which the spring force is released to act on the clockwise about its rocker pivot axis . The dog 80b and the 

rocker . This can also involve a releasing of the button 10 . cam 117b in this case act like a lever , which produces a 

In order to tension the strap B arranged between the counterclockwise torque about the rocker pivot axis 80a . tensioning wheel 87 and the tensioning plate 89 , the ring FIG . 9 shows the end position of the opened rocker . Here , gear 107 is clamped on its outer circumferential surface by 5 the planet carrier 117 turns in the opposite rotary direction 

way of the clamp 33 to prevent rotational movements . The as compared to FIG . 8 and thereby comes to bear against the 

planet carrier 105 is not clamped , and so it can turn , as can dog 80c of the rocker 80 . The dog 80c is situated in regard 

the connection shaft 8 . The motorized driving movement to the rocker pivot axis 80a and the other dog 80b on the 

from the sun gear 30 in the planetary gearing 106 arranged other side of the rocker pivot axis 80a . In the position of use 

on the tensioning axis 86a is transmitted through the planet 10 of the strapping device with a horizontal orientation of the 

carrier 105 and the ring gear 107 to the planet gears 114 of base plate , the dog 80b is situated above and the dog 80c 

the second planet carrier 115 and sets the latter in rotation below the rocker pivot axis 80a . In this way , the rocker 

A sun gear , not recognizable in the representation of FIG . 5 , swivels clockwise in the representation of FIG . 9 and 

drives the planet gears 121 of an additional downstream thereby creates a spacing from the tensioning wheel 87 . stage of the planetary gearing 106 . The planet carrier 122 of 15 FIG . 12 shows a partial perspective view of the tensioning 

this stage also rotates . The sun gear 123 of the last - men - apparatus of the second sample embodiment , in which only 

tioned stage is further led through the additional planet one of the two clamps is depicted . Here , the clamp 33 is 

carrier 117 and drives the planet gears 118 of this additional brought to bear against the flat circumferential surface 107b 

stage , which in turn are in engagement with an internal of the ring gear 107 , which is essentially round in cross 

toothing of the tensioning wheel 87 . The tensioning wheel 20 section . FIG . 13 shows a sectional representation through 87 is thus driven in the tensioning direction across the single the ring gear 107 and the clamp 33 . By way of the clamp 33 

or multiple - stage planetary gearing 106 and the inserted of the locking mechanism , the ring gear can be optionally 

strap B is tensioned . clamped against rotational movements or released again . In the previously described operating mode of “ tension . Each of the clampings provided in the strapping devices of 

ing ” , in which the tensioning wheel 87 engages with the 25 FIG . 2 - 11 can be configured according to the locking mecha 

strap B , a force of resistance in the form of a restoring nism described here , however traditional locking mecha 

moment acting from the strap B on the rotating tensioning nisms are also possible . In the clamping according to the 

wheel 87 is produced by virtue of the strap tension . Its present disclosure , an at least approximately planar circular 

magnitude is variable and proportional to the magnitude of or circular arc - shaped circumferential surface of the gear 

the applied strap tension . This force of resistance works 30 interacts with a pivoting clamping element or clamping 

opposite the motorized driving moment which arises in the body . The circumferential surface 107 of the sample 

gear elements participating in the transmission of the driving embodiment shown , functioning as a clamping surface , has 

movement . In the sample embodiment , the planet carrier 117 no detent elements with which a clamping is provided that 

is braced by a cam 117b , having the function of an end stop , is based on a form - fitting engagement of a clamping element 

against the rocker 80 . The planet carrier 117 rotating by the 35 with a detent element or a detent recess . motorized driving movement in a suitable rotary direction The clamping element 33 is mounted so that it can pivot lies by its cam 117b against a dog 80b of the rocker and about the shifting and pivoting axis 143 , where the shifting thereby turns it in a motion according to arrow 113 ( FIG . 6 ) axis 143 of the clamping element 33 runs parallel to the axis 

about the rocker axis 80a against the tensioning wheel of rotation of the gear 107 being clamped . The shifting axis 

Optionally , a noticeable rotary movement about the rocker 40 143 runs in the region of one end of the camlike clamping 

axis 80a will not actually be executed here , but essentially element 33 . In the region of the other end of the clamping 

only the torque about the rocker axis 80a is increased . In element there is provided an arc - shaped contact surface 33a , either case , however , the pressing force by which the rocker which is provided for a contact with the clamping surface 

80 presses the tensioning plate 89 or the strap against the 107b of the gear being clamped . Due to the circular shape of 

tensioning wheel 87 is increased . This increase generally 45 the clamping surface 109h as well as the arc shape of the 

does not occur in a single step . The increasing of the contact surface 33a inside view , an essentially linear contact 

pressing force of the rocker against the strap , ultimately comes into being when the clamping element 33 contacts the 

stemming from the motorized driving movement and the circumferential surface 107b , and this line of contact runs 

already existing strap tension and occurring by engaging perpendicular to the plane of the drawing in FIG . 13 . with the tensioning gearing 106 , occurs proportionally to the 50 As emerges from FIG . 13 , the clamping element 33 is 

resistance and restoring force present in the strap and acting arranged in relation to the gear 107 being clamped such that 

as a resistance force against a maintaining and a further the line of contact of the contact surface 33a has a distance 

increasing of the strap tension at the point of engagement 155 from its pivot axis 143 which is greater than the distance 

with the strap , from the strap to the tensioning plate 89 and of the pivot axis 143 from the clamping surface 107b . As a 

on the tensioning wheel 87 . As long as an increasing of the 55 result , during a pivoting motion of the clamping element 33 

strap tension is occurring by the tensioning process , so too from its release position to a clamping position it already 

will the resistance force increase and thus the pressing force comes into contact with the clamping surface 107b at a point resulting from it . which lies before a line of connection 156 of the axis of 

In FIGS . 8 and 9 are shown the end positions of the rocker rotation of the gear 107 to the pivot axis 143 of the clamping 

80 which are possible on account of the swiveling ability of 60 element . In relation to the intended rotary direction 157 of 

the rocker to open and close on the one hand and to increased the gear 107 being clamped , the line of contact occurs before 

the pressing force on the strap on the other hand . As shown the imaginary ) line of connection 156 . The rotation of the 

in FIG . 8 , in one of the two end positions the tensioning plate gear 107 is braked and can at most still move just a little . 89 by virtue of a contacting of the cam 117b of the planet Thanks to a further rotation against the increasing clamping 

carrier 117 with a contour of the dog 80b and a clockwise 65 action , the clamping action is further intensified and an 

rotational direction of the planet carrier ( in relation to the increasing wedging of the clamping element 33 against the 

representation shown in FIG . 8 ) rotates the rocker counter - gear 107 is intensified . Thanks to these geometrical rela 

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US 10 , 370 , 132 B2 

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tions , the clamp 33 cannot pass the line of connection 156 15 storage battery in rotary direction of the gear , its pivoting motion halts 19 bevel gear 

before the line of connection 156 and presses against the 20 bevel gear clamping surface 107b . In an end position essentially cor - 21 gear responding already to the position of first contact with the 5 22 toothed belt drive 

clamping element 33 , the gear 107 is clamped against the 23 gear 

camlike clamping element 33 . No further movement is 24 shaft 

possible , regardless of how high the torque is . 25 planet carrier 

FIG . 14 shows the geometrical relations of the clamping . 25a clamping surface 

Here as well , the connection between the axis of rotation 86a 10 25b planet gears of the gear 107 and the pivot axis 143 is designated as 156 . 26 gearing 

The contact surface ( circumference ) of the gear could be 27 ring gear 

smooth or structured . The radius of the gear at the contact 27a shoulder 

site with the cam is designated as 158 and the pivot radius 27c cam 

of the clamping element 33 at the contact site is 155 . The 15 28 roller bearing pivot radius 155 at the contact site subtends an angle a with 29 first clamp 

the line of connection 156 , and the radius 158 of the gear 107 29a arc - shaped contact surface 

an angle y with the swivel radius 155 ( each time at the 30 sun gear contact site ) . In the sample embodiment , the geometrical 31 axis of rotation of gearing and tensioning wheel 

relations are such that in the clamping position , in which the 20 32 ring gear 

gear 107 is blocked against rotational movements in the 32a outer surface 

intended rotary direction , the angle y is at least approxi 33 second clamp mately 155o . In experiments it was also possible to achieve 34 planet gear 

good results when using an angle from the range of 130° to 35 planet carrier 

170° , especially from 148° to 163o . The angle a should 25 36 sun gear advantageously be greater than or equal to 7o . In the sample 37 planet carrier 

embodiment , it is 9o . In other embodiments , it can also be 37a shoulder 

chosen from a range of 7° to 40° . 38 planet gear 

In the sample embodiment of the present disclosure 39 stop element 

discussed here , it is not absolutely necessary , if the wedge 30 40 arrow 

effect is strong enough , to maintain the position of the cam 41 planet gear in its clamping position by outside measures . This already 42 planet carrier 

occurs simply due to the fact that the gear 107 can only turn 43 sun gear in one rotary direction and this is in fact blocked in remov - 44 spring element ( restoring spring ) able fashion by the clamp 33 . In sample embodiments of the 35 45 freewheeling 

present disclosure , the camlike clamping element is held in 46 abutment 

position by the spring force of a spring element 159 . For this , 46a recess 

the spring element 159 lies against the clamping element 80 pivoting rocker 

above the shifting axis 143 and turns or holds the clamping 80a rocker pivot axis 

element 29 in its clamping position . In order to remove the 40 80b dog clamping element from its clamping position , the spring 80c dog force must be overcome with a switch 160 . Using the switch 86 tensioning apparatus 160 , both clamps 29 and 33 can be activated at the same 86a tensioning axis 

time . Depending on the arrangement of the switch / button , a 87 tensioning wheel 

pulling or pressing of the switch can overcome the spring 45 89 tensioning plate 

force and release the ring gear 107 from the clamp 33 and 99 bevel gear 

lock the planet carrier 105 . In the other movement of the 100 bevel gear switch / button , the clamp 29 and the planet carrier 105 are 105 spur gear ( planet carrier ) again released via the spring force , while the clamp 33 locks 105b planet gear the ring gear 107 . 50 106 gearing 107 ring gear 

LIST OF REFERENCE SYMBOLS 107b circumferential surface 109 ring gear 1 strapping device 109b circumferential surface 

2 housing 55 109c external toothing 

3 handle 110 sun gear 

4 base plate 112 arrow 

6 tensioning apparatus 113 arrow 

6a tensioning axis 114 planet gears 7 tensioning wheel 60 115 planet carrier 

8 rocker 117 planet carrier 

8a rocker pivot axis 117b toothing 9 tensioning plate 117a cam 

10 button 117b cam 

12 friction welding mechanism 65 117c toothing 

13 welding shoe 118 planet gear 14 transmitting mechanism 121 planet gear 

Case 2:24-cv-00080-JRG Document 57-9 Filed 10/17/24 Page 23 of 24 PageID #: 1439
US 10 , 370 , 132 B2 

19 20 

122 planet carrier 3 . The strapping device of claim 2 , wherein the first angle 123 sun gear is selected from a range of approximately 140 degrees to 

124 spring element approximately 165 degrees . 125 freewheeling 4 . The strapping device of claim 2 , wherein the first angle 143 shifting axis 5 is selected from a range of approximately 149 degrees to 150 circular arc segment approximately 162 degrees . 150c toothing 5 . The strapping device of claim 2 , wherein the first angle 151 connection shaft is selected form a range of approximately 152 degrees to 151a connection axis approximately 158 degrees . 155 distance / swivel radius 6 . The strapping device of claim 1 , wherein , in the locking 156 connection line position , a swivel radius of the clamp at a contact point of 157 rotary direction the clamp and the peripheral clamping surface of the gear 158 radius element makes a second angle with a line connecting an axis 159 spring element 

160 switch is of rotation of the gear element and the clamp axis of the 

B strap clamp , the second angle selected from a range of approxi 

M motor mately 5 degrees to approximately 25 degrees . The invention is claimed as follows : 7 . The strapping device of claim 6 , wherein the second 

1 . A strapping device for strapping packaged goods with angle is selected from a range of approximately 7 degrees to 

wrapping strap , said strapping device comprising : 20 approximately 15 degrees . a base ; 8 . The strapping device of claim 6 , wherein the second 

a rocker pivotably mounted to the base about a rocker angle is selected from a range of approximately 7 degrees to 

axis ; approximately 10 degrees . a tensioning wheel supported by the rocker , the tensioning 9 . The strapping device of claim 1 , wherein , in the locking wheel being rotatable about a tensioning axis and 25 position : 

engageable with the strap ; a swivel radius of the clamp at a contact point of the clamp gearing operatively connecting a motor to the tensioning on the peripheral clamping surface of the gear element 

wheel to transfer a driving movement from the motor to makes a first angle with a line connecting the clamp the tensioning wheel , the gearing comprising a rotat axis to an axis of rotation of the gear element , the first able gear element ; and angle selected from a range of approximately 152 

a locking mechanism configured to lock the gear element , degrees to approximately 158 degrees ; and the locking mechanism comprising a clamp that is the swivel radius of the clamp at the contact point of the arranged at a distance from the gear element , the clamp clamp and the peripheral clamping surface of the gear being pivotable about a clamp axis from a release element makes a second angle with a line connecting position to a locking position in which the clamp bears 35 

against a peripheral clamping surface of the gear ele the axis of rotation of the gear element and the clamp axis of the clamp , the second angle selected from a ment , wherein the clamp has a pivot radius greater than 

a distance from the clamp axis to the peripheral clamp range of approximately 7 degrees to approximately 10 

ing surface of the gear element , and rotation of the degrees . 

clamp about the clamp axis during movement from the 40 10 . The strapping device of claim 1 , which comprises a 

release position to the locking position occurs in a tensioning plate supported by the base . 

direction of rotation opposite that of the gear element 11 . The strapping device of claim 10 , which comprises a 

being clamped . biasing element configured to bias the rocker to a position in 

which the tensioning wheel contacts the tensioning plate . 2 . The strapping device of claim 1 , wherein , in the locking position , a swivel radius of the clamp at a contact point of 45 12 . The strapping device of claim 11 , wherein the biasing 

the clamp on the peripheral clamping surface of the gear element comprises a spring . 

element makes a first angle with a line connecting the clamp 13 . The strapping device of claim 1 , which comprises a 

axis to an axis of rotation of the gear element , the first angle connecting device drivable by the motor to connect two 

selected from a range of approximately 120 degrees to overlapping portions of the strap to one another . approximately 170 degrees . 

30 

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