US2111115A - Wire tying machine - Google Patents

Description

March l5, 1938.

H. J. GIBBS ET Al.

WIRE TYING MACHINE Filed Aug. 11, 193e 5 Sheets-Sheet l @j THOMAS A, BmeHAM DAvJD W. BINGHAM ATTORNEY arch 15, 1938'. H. J. GIBBS ET A. '2,111,115

WIRE TYING MACHINE Filed Aug. ll, 1936 5 Sheets-Sheet 2 A mvgmoRs 96 @i HAROLD J. Gls

THOMAS A." BINGHAM D'Avm W. BWGHAM BY ATTORI/viv March l5, 1938. H. J. Glass ET A1. ZM

WIRE TYING MACHINE FiledAug. 11, 1936 5 Sheets-Sheet 3,y

NVENTORS HAROLD J.. GIBBS THOMAS A. BINGHAM DAVID W. BINGHAM Bq M@ @Mob ATToR/yrfy Emi-1938. H. .1 Glass Er AL nlug l WIRE TYING MACHINE y l @1% MENTORS HAROLD J. 6:31155l THOMAS A. BINGHAM DAVIUW. BINGHAM 'Bv M Arran/wy' March l5, 1938.

H. J. GIBBS ET AL 2,111,115

WIRE TYING MACHINE 5 Sheets-Sheet 5 Filed Aug. ll, 1936 NVENTORS HAROLD J. GIBBS THOMAS A. BWGHAM DAVID BINGHAM' Patented Mar. 15, 1938 UNITED STATES PATENT OFFICE 2,111,115 WIRE TYING MAoiuNE Melbourne, Australia Application August 11, 1936, Serial No. 95,448 In Australia August 16, 1935 Y v 26 Claims.

This invention relates to wire tying machines of the kind wherein wire led round a case or the like to be bound is tensioned and the overlapped ends or portions of the wire are secured together by twisting one around the other.

. The general object of the invention is to pro-- vide a wire tying machine adapted for, and equipped with hand or power operating mechanism whereby Wire binding operations may be performed eiiciently and rapidly with a minimum of manual attention, the various functions of the machine being carried out automatically in proper sequence, thus permitting a high rate of output.

More specific objects of the invention are:- to provide a power operated wire tying machine adapted to be brought into action by a clutch device which is readily operable manually by an operator incidental to his placing wire in operative position through the machine and around a case or the like; to provide a wire tying machine in which relatively small and detachable parts such as springs, pawls, latches and the like are eliminated or reduced to a minimum; to provide a wire tying machine in which the functions of tensioning, twisting and cutting the wire are brought about by and during continuous turning of a main shaft in one direction, and preferably during one complete revolution of the shaft, until the parts arrive in positions ready to repeat the cycle of operations; to provide improved wire tension means in which the wire is sub-jected to equal amounts of tension at opposite sides of the twisting means and in which the tension action is purely linear or straight line and is effected by a force whichis constant and uniform for the entire tensioning action; to provide ample compensation for the tension means in order to avoid overstrain and fracture of the wire by spring means of such form and dimensions as will effectively withstand stresses and fatigue due to constant use and in which the stresses are evenly distributed throughout the spring means; to provide means by which the amount or degree of tension may be innitely varied by a simple adjusting operation; to provide a wire tying machine capable of ready adjustment to give variation in the number of twists imparted to the wire to provide a machine which ensures that the portions of the wires extending between the opposite twist portions will lie iiat in side by side attitude upon the case or -box being bound; to pro-vide a machine in which cutting of the wire takes place after completion of the twisting operation and is effected by positively actuated means devoid of springs or other extraneous members liable to breakage or disorder; to provide power operating mechanism from which driving energy is supplied tothe machine and also to means synchronized with the operation of the machine so as to 'eliect relative movement between the case or the like and the machine at the completion of binding operations to thereby facilitate delivery or replacement of the case or the like; to provide counterbalanced supporting means for the machine, case moving means and power operating mechanism whereby the machine is rendered more convenient in operation and control and is capable of giving a relatively high rate of output.

The foregoing and various other objects and features of the invention and the advantages arising therefrom will however be more readily appreciated from the following description of one practical embodiment, it being understood that various modifications, additions and/or renements may be incorporated without departing from the spirit and scope of the invention as dened by the appended claims.

Referring to the drawings which form part of this specification:-

Figure 1 is a side elevation showing a power operated machine with supporting means and case ejecting mechanism according to the invention.

Figure 2 is a plan of Figure 1 in which certain parts are broken away for convenience of illustration.

Figure 3 is a front view of the machine on a larger scale.

Figure 4 is a plan of the machine.

Figure 5 is an elevation of the main shaft with associated parts in section.

Figure 6 is a cross section on an enlarged scale on line VI-VI of Figure 5.

Figure 7 is a right hand end View of the machine.

Figure 8 is a left hand chine.

Figures 9, l0 and ll are side views of the twisting means and cam devices associated therewith and illustrating the overthrow and automatic return action of the twisting means.

Figure 12 isla front elevation of a power gripper.

Figure 13 is a plan of Figure 12.

Figure 14 is a cross section of line XIV-XIV of Figure 13.

Figures 15 and 16 are developed views of the end view of the maleft and right hand cams, respectively, of the main shaft.

Figure 17 is a front view of the twisting means, with a bearing cap removed.

Figure 18 is a section on line XVIII-XVIII of Figure 1'7 including the bearing cap.

Figure 19 is an end View of the left hand cutter and actuating means.

Figure 20 is a fragmentary left hand end view showing clutch operating means for connecting a lay shaft to a power operated shaft and means for suddenly arresting rotation of the main shaft of the machine.

Figure 21 is an elevation of the lay shaft with associated parts in section.

Figure 22 is a perspective view of the left hand gripper.

Figure 23 is a cross section on line A--A Figure 4.

Figure 24 is a cross section on line B-B Figure 4.

Figure 25 is a cross section on line C-C Figure 4.

A machine in accordance with the invention has a suitable base plate 2 capable of resting upon a case or other object to be bound. Bearing brackets 3 with detachable caps 4 may upstand from the base at appropriate positions adjacent to the front edge of the base to support a shaft hereinafter referred to as the main shaft, from a single revolution of which all essential functions, i. e., tensioning, twisting and cutting of the wire, are derived.

Left hand and right hand wire gripping devices indicated generally by the numerals 'l and ii are provided one at each side of the twisting device, and these two grippers are adapted to be moved away from each other with a straight line motion to tension the wire. For this purpose the grippers may be mounted upon slides 3, i l guided by pairs of guide rods l2, I3 aiiixed to the base 2. The tension slides are provided with rollers I4 for (2o-operating with two cam members i6, il, on the main shaft by which the gripper carrying slides are moved in unison to tension the wire.

Each said cam member is preferably in the nature of a cylindrical collar connected to the shaft by splines i8 enabling the collar to move axially along the shaft. Each collar is provided around its periphery with a channel or cam track the sides of which are engaged by the roller on the respective slide. The track T of each cam member is endless and as best seen in Figures l and 16 has commencing from the neutral point N a spiral portion I9 which produces outward movement of the respective slide, and which merges at one end into a purely circumferential portion 2l which holds the respective slide in its outward position while the tensioned wire is being twisted, and a return portion 22 which may curve or extend spirally to neutral point N so as to cause the respective slide to return to its inward position after completion of the twisting action. Such return action may be assisted if so desired by spring means (not shown).

Each cam or collar I3, il may have an axial recess 23 extending for a suitable distance from its inner end to accommodate a coiled spring 24 which encircles the main shaft 6 between a face or shoulder 26 terminating said recess and an adjustable enlargement 2l' such as a washer or disc backed by a nut 28 engaging a screw threaded portion 2S of the main shaft. The two springs associated with the cam members provide a compensating action during the tensioning of the wire which avoids excessive tension eifort being applied to the wire. It will be evident that any stresses imposed upon these springs during the tension operation will be distributed uniformly throughout the springs. Consequently by making the springs of adequate dimensions, for example, of about one and a half to two inches in diameter, and of appropriate cross section and length, they will effectively withstand repeated use and remain free of fatigue. Innitely variable adjustment of the amount of tension may be obtained by adjusting the nuts 28.

The right hand gripping device is preferably so arranged as to grip the Wire with power derived from operation of the associated tension cam ll. For this purpose the track engaging roller l for cam il, as best seen in Figures 12, 13, and 14 may be mounted about a stem 3l upstanding from one end of a gripper lever 32 intermediately pivoted, as by pin 33, to tension sli-de li and having at its front end a gripper 3ft disposed adjacent an anvil 3G which may be formed by a replaceable member detachably secured to a lug :il` at the front of the slide Il. Pivotal movement of lever 32 and gripper 34 may be limited by flanges 3S upstanding from the slide at the sides of the lever. With such an arrangement it will be seen that there may be a certain degree of lag in the outward movement of slide El relative to its cam IT such lag being taken up by swinging movement of the gripper lever 32 in a direction to swing the gripper 311 to the left so that it more tightly grips the wire. This grip is so efficient that it may not be necessary for the 4gripper to be serrated, or if serrated, the serrations need only be of comparatively slight depth and devoid of sharp edges. The co-acting face of anvil 35 may if desired be similarly serrated.

Such gripping means will not deform, bend or bite into the wire which is important for the reason that the gripped portion will after completing of the cycle of operations form part of the twisted portion in the next cycle of operations and, being unweakened, will effectively stand the tensioning and twisting operations.

The left hand gripping device may be similar to to the right hand device but as the portion of the wire held by the left hand device is discarded after cutting it is not so important. Thus a simpler gripping device as seen in Figure 22 may be employed at the left hand side of the machine. This device comprises a jaw 3l fixed between lugs 3S outstanding from slide 9 and dis- -vided with hollow outstanding trunnions 4"! (see Figures 17 and 18) fitting in slotted sleeves 48 partly accommodated in recesses 49 in the front of the base 2 and retained in position by projections 50 of a bearing cap 5l attached to bearing brackets 3.

A segmental driving gear 52 on the main shaft 6 meshes under certain conditions with a smaller erl 'completely toothedgear 53 una ylay spindle 54 which also carries another completely toothed and larger gear 56 meshing with the twister pinion. rIhe lay spindle 54 may be journalled in bearing sleeves l partially accommodated by recesses in bearing brackets 3 and by the bearing cap 5l. v The segmental driving gear 52 may have a cam V5i! at one side which co-operates with a cam 59 on lay spindle 54 in such manner-'that the latter and consequently the twisterpinion are prevented from rotation at all periods other than when twisting is taking place, the segmental gear during such periods passing idly by its' associated driven gear 53. After completing the required number of twistsv the twister pinionis further revolved through a ksn'iall arc, still being driven by the gears.- Then the camsf58 59, cause the twister pinion. to turn in reversethrough a corresponding arc so that the slot of the pinion is aligned with the wire-way o-f the machine. This overthrow of the twister pinion and automatic reverse movement ensures thatthe overlapped untwisted portionsY of the. wire will lie flat in side by side formation upon the box or case when the machine is freed from the tied wire binding. Y v

Various cam arrangements -may be adopted to produce the before mentioned actions. According to the illustrated form (see Figures 9, 10,' and 11) the segmental gear 52 is toothed vfor about one half .of its periphery and the cam. 58` vof this gear has a semi-circular face .58ay concentric and coterminous with the toothed portionof the main gear. This semi-circular face may merge at one end by an approximately tangential face 58h into an end of a larger diameter,.and slightly less than semi-circular face 53C which is joined at its other end to the face 58a by a short somewhat radial face'58d. The other -cam 59 has a face 59a which is circular with the exception of a concave chordal portion 59h, the curvature of which conforms to the curvature of the larger diameter semi-circular face 58o of cam 53.

At the commencement of each cycle oi' operations', the untoothed portion .of the segmental gear is adjacent the associated gear 53 while'the concave chordal face 5927 ofthe second cam is in engagement with the major semi-circular face 58e of the rst cam as in Figure 9 whereby the second cam and lay spindle 54 are prevented from rotation without however impeding rotation of the rst cam. During this stage the `wire is being tensioned and the twister pinion 46 is of course idle. As the .tension action isv completed the segmental gear` commences to mesh with gear 53 while the smaller semi-circular face 58a of the rst cam 58 comes opposite the concave face 59h of the second cam 59, as in Figure thus freeing the second cam, the lay spindle 54 and the twister Apinion for rotation. The overlapped wires-which pass through slotted wire receiving jawsV 6l at opposite sides of thetwisting device, are thus twisted together by the positive 4drive from the main shaft through the gear train 52,53, 56 to the twister pinion which continues until the toothed portion of the segmental gear recedes from gear 53. As this commences to take place, the substantially tangential vface 58h of the first cam engages the concave face 59h of the second cam and causes the latter and consequently the lay spindle and twister pinion to be turned slightly in the reverse direction; as in FigureV 11 thus returning'the twister pinion 46 into such a position that itsslot is aligned with the wireway of the machine. After this reverse movement of the lay spindle and twister pinion has been completed, the second cam 59 and associated parts are again locked in position by the col-operation of the major semi-circular face 58e of the rst cam and the concave face 59h of the second face, until vsuch time as the major `semi-circular face 58o' recedes from the concave face 59h as previously described.

The number of twists effected by the twister pinion may be readily varied by selection of a segmental gear`52 and driven gear 53 having an appropriate number ofv teeth, such change being the only one necessary to adapt the machine for three, four or more twists.

Cutting devices, one at the outer side of each wire receiving jaw 6l, may be brought into operation automatically after completion of the twisting operation. -These cutters are preferably devoid of springs and arranged to be positively operated, both on their active and return movements, from the main shaft 6. For this purpose the main shaft may have two cutter cams, reach advantageously in the form of a collar 63 with a cam track 63a in a side face for accommodating a roller 64 on a pin 66 projecting fro-m a plate 61 pivoted about a pin' 69 to the base of the machine, the plate carrying a cutter blade 69 located-adjacent the respective wire receiving jaw. By arranging for the cutters to come into operation after the completion of the twisting action, instead of during the operation, it is'ensured that the torsional stresses are prevented from being concentrated at the outer ends of the two twisted portions and, owing to the distribution of such stresses, the wire is not weakened at any one point. Furthermore, the cut ends of the wire will not project outwardly but will lie snugly against o-r contiguous with the adjacent portions of the wire and also lie flat upon the top of the box.

The main shaft 6 may be adapted for manual operation or may be driven from any suitable source of power. In a preferred arrangement it receives its drive from an electric motor ll through the medium of variable reduction gearing, located in casing l2, a constantly rotated shaft i3 and a clutch device 14 winch is adapted to be thrown in by the operator, and to be automatically thrown out as the shaft 6 completes each revolution.

The main shaft 6 may therefore be provided at its right hand end with a freely mounted spul` gear 16 meshing with a companion gear 'il rotatable about a lay shaft 'i8 and fast with a bevel wheel 19 which meshes with a bevel pinion 8| connected to the constantly rotated power driven shaft 13 which extends rearwardly of the machine. The lay shaft i8 extends parallel with and tothe rear of the main shaft and is supported by bearings 82 upstanding from base 2 and provided with detachable caps 83.

According to one form, the clutch device 'i4 comprises a key member 85 (Figs. 5 and 6) adapted to be projected by a Vspring 85 through a radial slot 8l in the main shaft into any one of a num.- ber of recesses 88 formed in the interior of the freely mounted spur gear '56. A lever 99 may be pivoted to lugs 9| outstanding from a bearing bracket 92 supporting the power operated shaft 'i3 and may be acted upon by a spring plunger 93 tending to maintain the lever in normal position. A forked end of lever 89 may be connected Y to asleeve 94 which is slidable lengthwise on the main shaft and has an internal spiral cam face provided to cushion downward swinging of the 96 adapted to co-operate with the aforesaid key member 84.

The clutch 14 is thrown into operation manually by suitable means .conveniently located at the front of the machine and which may comprise a, horizontal rocker spindle 91 journalled in bearings 98 carried by certain of the bearing caps 4 and 83 and provided at each end with upstanding arms 99 bridged by a horizontaloperating bar or rod At its right hand end the rocket spindle carries a cam member |02 having a cam face |03 aligned with a roller |04 disposed between a forked projection |06 of lever 89. Upon the operator pushing the bar |0| downwardly and rearwardly (against the influence of a spring pressed plunger |00 acting against a projection 99a of one of the arms 99 as in Figure 25) the cam face |03 causes lever 89 to turn about its pivot so that sleeve 94 by its movement along the main shaft enables key 84 to be spring projected to the key engaged in the first recess 88 of the freely mounted gear 16 which comes opposite to the key, whereby the main shaft 6 becomes coupled to the power driven shaft 13. Soon after the main shaft 6 commences to rotate the wide part of the sleeve cam face 96 comes opposite the head of the key member 84 so that the sleeve 94 due to spring plunger 93 and lever 89 moves lengthwise on the shaft over the key 84 whereby the latter is gradually depressed by the spiral cam face 96 with the result that the main shaft after making one complete revolution is disconnected from the power driven shaft.

If desired, the sleeve 94 may have a second cam face |01 co-operating with a projection |08 on the main shaft 6 to prevent the lever 09 from being held by an operator in such a position as would prevent the automatic tripping of the clutch at the completion of a single revolution of the main shaft.

The machine, the power driving mechanism, and means for effecting relative movement between the machine and a. case at the completion of a binding operation, are preferably mounted upon a tiltable or see-saw frame o-r support so that the machine normally assumes a position with its base 2 slightly clear of the case. This facilitates positioning of cases or the like beneath the machine preparatory to wire binding operations, the normal operations of placing wire around the case and through the machine and the subsequent tensioning of the wire causing the machine to rest securely upon the upper face of the case.

For this purpose, a pair of bars (Figures 1 and 2) may be secured at their front ends to the machine base and at their rear ends to a plate 2 upon which the electric motor 1| l and reduction gearing are mounted. Intermediately of their length the frame bars may have bearings H3 for an axle ||4 supported by a head piece ||0 vertically adjustable upon a pillar or stand H1. This stand, which is shown as comprising a T-section bar, may have a toothed rack 8 engaged by a worm pinion ||9 supported in the head piece I6 and operable by the cranked end |20 of spindle |2I.

The see-saw frame may be counterbalanced as by a spring |22 connected at its upper end to plate ||2 and at its lower end to a bar |23 depending from the head piece. A buffer device, comprising for example a spring |24 supported beneath the rear end of plate ||2 from a rearward projection ||6a of head piece IIB, may be rear part of the see-saw frame.

To permit of rapid and easy separation of the machine from the driving motor, the power driven shaft 13 may have squared end portions 13a respectively fitting into the bevel pinion 8| and a collar |26 of a spring loaded clutch |21 that connects shaft 13 to the power driving unit.

Relative movement between the machine and a bound case at the completion of a binding operation is preferably effected by case pushing mechanism actuated by lay shaft 18, which is brought into action automatically as the main shaft 6 of the machine completes each revolution. Accordingly the left hand end of the main shaft 6 may have a cam like striker |28 adapted as the main shaft is nearing the end of each revolution to engage a roller |29 supported from a spindle |3| adapted to slide lengthwise in bearings |32, whereby the spindle is moved to the left against the influence of spring |33. At its other end the spindle may be connected by lever |34 (Fig. 23) to a sleeve |35 of a clutch device |36 adapted to couple the power driven gear 11 to the lay shaft 18 and to automatically trip itself as the lay shaft completes a revolution. Clutch device 36 may be identical in all material respects with clutch device 14 previously referred to and illustrated in Figs. and 6 and wherein sleeve 94 is the counterpart of sleeve |35 of the lay shaft clutch device.

In order to ensure that clutch 141s tripped before clutch |36 connects the lay shaft 18 to the power driven shaft 13, and also to definitely arrest rotation of main shaft 6 with the slot of the twister pinion correctly aligned with the wireway of the machine, the main shaft is shown at its left hand end' with a disc |31 with a peripheral hump |38 disposed in the path of a roller |39 (Figs. 8 and 20) on the free vend of an arm |40 pivoted to the base 2 and urged towards the disc |31 by a spring pressed plunger |4|. The relatively steep end of hump |38 comes adjacent roller |39 just before main shaft 6 completes each revolution, whereby the nal stage of rotation of shaft 6 is effected or assisted by the spring pressed arm |40, and the roller immediately snaps home behind the st eep part of the hump |38 into a depression |42 of disc |31 so as to' prevent any backlash or inadvertent turning of shaft 6.

The lay shaft may have a disc |43 with eccentric pin |44 to which is connected the forward end of a rod |46 connected at its rear end, as by the screw threads |41 and nuts |48 to a block |49 held by a screw |5| between two legs of a case pushing member |52. Member |52 is pivotally connected intermediately of its height to the seesaw frame, as by means of a pivot pin |53 supported by a bar |54 bridging the bearings ||3, and provided at its lower end with a pad or the like |56 adapted to engage the rear end of a case |51 being bound. It will be evident that upon throwing in of the clutch |36 the lay shaft 18 will make one complete revolution before being tripped during which period the connections between the lay shaft and the case pusher member |52 will cause the lower end of the latter to swing forwardly and push the case forwardly so as to free the bound wire from the machine and allow the latter to rise clear of the case.

The amount of swinging movement of the case pusher |52 may be readily adjusted by means of the nuts |48 and also by means of the adjusting holes |58 in the pusher member for the screw |5| A brake device comprising a brake band |59 with screw adjusted spring influenced tension means |60 may co-operate with a disc I6! on the lay shaft in order to prevent the lay shaft from turning beyond one complete revolution during each cycle of operations.

The gears 16, 11, 19- and 8| may be protected by guard |65 as best seen in Figs. 3, 4, 24 and 25, and the front of the guard may be in substantial longitudinal alignment with the wireway of the machine and the gripping members 134, 36, of the right hand gripping device 8 to thereby act as a guide facilitating the insertion of the trailing end of a wire between members 34 and 35.

Having now described our invention what we claim as new and desire to secure by Letters Patent is- 1. In a wire tying machine, a shaft, wire tensioning means comprising cam members capable of lengthwise movement on said shaft, means yieldingly opposing such lengthwise movement in one direction, a wire twisting device, two slides operatively associated with the respective cam members for gripping wire at opposite sides of said wire twisting device, whereby upon continuous turning of said shaft the wire is tensioned by a substantially straight line motion and for substantially equal amounts at each side of the twisting device.

2. In a wire tying machine the combination claimed in claim 1 wherein each cam member consists of a collar having a peripheral cam` track adapted to co-operate with a member of the respective slide, and has an associated coiled spring encircling said shaft and bearing at one end against said cam collar and at its other end against a stationary abutment.

3. In a wire tying machine having a wire way extending at the front thereof, wire twisting means, a shaft, wire tensioning means, comprising two cam members mounted upon said shaft with ability for lengthwise movement thereon, spring means o-pposing such lengthwise movement in one direction, two slides operatively associated with' the respective cams and adapted to be guided for movement lengthwise of the wire way of the machine, and devices on the respective slides for gripping wire at opposite sides of said wire twisting means, whereby upon continuous turning of said shaft the wire is tensioned by a substantially straight line motion and for substantially equal amounts at each side of the twisting means.

4. In a wire tying machine the combination as v claimed in claim 3 wherein each cam has an endless cam track having a partly spiral portion which produces outward or tensioning movement of the associated slide, a circumferential portion which functions to hold the slide stationary while the tensioned wire is being twisted, and a return portion which unites said iirst mentioned two portions and permits or causes the slide to return to its normal position after the tensioned wire has been twisted.

5. In a wire tying machine, the combination claimed in claim 3 in combination with' means for actuating said wire twisting means comprising a segmental toothed gear and a cam fast on said shaft, a lay spindle, said spindle having a rst toothed gear aligned with said segmental gear, a second toothed gear adapted to mesh with a slotted pinion of said wire twisting means, and a cam ,co-operating with said cam fast on said shaft, said two latter cams being so formed as to lock the lay spindle against rotation except ,l when the wire twisting action is taking place,

and the slotted pinion at the termination of the twisting action.

6. In a wire tying machine, the combination claimed in claim 3 in combination 'with means vfor actuating said wire twisting means comprising a segmental toothed gear and a cam nfast on said shaft, a lay spindle parallel with said shaft, said spindle having a rst toothed gear aligned with said segmental gear, a second toothed gear adapted to mesh with a slotted pinion of said wire twisting means, and a cam co-operating with said cam fast on said shaft, said last mentioned cam having an approximately semi-circular face concentric and'coterminous with the toothed portion of said segmental gear, a tangential face connecting said semi-circular face at one end to an end of a larger diameter` and slightly less than semi-circular face which is connected at its other 'end to the other endof said first mentioned semi-'circular face by a substantially radial face, the companion cam on said lay spindle being circular with the exception o'f a chordal portion of concave curvature complementary to that of said second mentioned semi-circular face of the cam that is fast on said shaft.

7. In a wire tying machine, the combination claimed in claim 3 in combination with wire cutters located one at each side of said wire twisting means between same and the respective tension slides, and cam means on said shaft timed for actuating said cutters upon completion of the wire twisting' action.

8. In a wire tying machine having a wire way, wire tensioning means comprising two cam members mounted upon a shaft, two slides operatively associated with the respective cams and adapted to be guided for movement lengthwise of the wire way ofthe machine, a wire twisting device, and gripping devices on the respective slides for gripping Wire at opposite sides of said wire twisting device, whereby uponcontinuous turning of said shaft the wire is tensioned b-y a substantially straight line motion and for substantially equal amounts at each side of the twisting device, at least one of said gripping devices being adapted togrip the wire with power derived from operation of an associated cam member and without deforming, bending or biting into the wire, said gripping device comprising an anvil on one of said slides, a lever pivoted to said slide and provided at one side of the pivot with a pin cooperating with a` track of one of said cam members, and provided at the other side of said pivot with a gripper cooperating with the anvil on said slide.

9. In a wire tying machine having a wire way, wire tensioning, wire twisting and wire cutting devices, a main shaft extending parallel with the wire way of the machine, and direct operative connections between said devices and said shaft whereby said devices are automatically actuated to tension, twist and cut the wire during a single revolution of the shaft which results in said devices being returned into their normal positions ready to repeat the cycle oi operations.

10, In a wire tying machine having a wire way,` wire tensioning, wire twisting, and wire cutting devices, a main shaft extending parallel with the wire way of the machine, direct operative connections between said devices and said shaft whereby said devices are automatically actuated to tension, twist and cut the wire during a single revolution of the shaft which results in said devices being returned into their normal positions ready to repeat the cycle of operations, and

mechanism adapted, upon completion of each cycle of tensioning, twisting and cutting operations, to effect relative movement between the machine and a case or the like that has been bound, in order to disengage the binding wire from the machine and facilitate the removal or' replacement of the bound case in relation to the machine.

11. In a wire tying machine, the combination claimed in claim 10, and including means for driving said main shaft and said mechanism for effecting relative movement between the bound case and the machine from a common source of power, and means for automatically transferring the drive from said main shaft to said mechanism upon completion of said cycle of wire tensioning, twisting and cutting operations.

12, In a wire tying machine, the combination claimed in claim 10 and including a lay shaft for actuating said mechanism for moving a` case relative to the machine, a constantly rotating power driven shaft, manually operable means for operatively connecting said main shaft to said power driven shaft so that the main shaft takes the drive for a predetermined period at theV expiry of which it is automatically disconnected from the power driven shaft, and means adapted to automatically connect said lay shaft to said power driven shaft at or about the time that said main shaft is disconnected from said power driven shaft.

13. In a wire tying machine, the combination claimed in claim 10 and including a lay shaft for actuating said mechanism for moving a case relative to the machine, a constantly rotating power driven shaft, a clutch manually operable to connect said main shaft to the power driven shaft and adapted to automatically trip itself to thereby free the main shaft from the power driven shaft after the wirev has been tensioned, twisted and cut, and a second clutch, operable through the agency of said main shaft at or about the time that the latter is freed from the power driven shaft, for connecting said lay shaft to said power driven shaft, said second clutch being adapted to trip itself to thereby free the lay shaft from the power driven shaft after said case moving mechanism has performed its function.

14. Improvements in and relating to wire tying machines, comprising wire tensioning, wire twisting and wire cutting devices, a main shaft, operative connections between said shaft and said wire tensioning, twisting and cutting devices, mechanism for effecting movement between the machine and a case that has been bound, a lay shaft for actuating said mechanism, a constantly rotating power driven shaft, a clutch manually operable to connect said main shaft to the power driven shaft and adapted to automatically trip itself to thereby'free the main shaft from the power driven shaft after the wire has been tensioned, twisted and cut, and a second clutch, operable through the agency of said main shaft at or about the time that the latter is freed from the power driven shaft, for connecting said lay shaft to said power driven shaft, said second clutch being adapted to trip itself to thereby free the lay shaft from the power driven shaft after said case moving mechanism has performed its function.

15. Improvements in and relating tol wire tying machines comprising a frame tiltably mounted intermediate of its length to a support, a wire tying machine attached to the front of said frame,

a power driving mechanism mounted on the rear of said frame having a driving shaft extending forwardly to said wire tying machine, and mechanism adapted to be actuated by said driving shaft for effecting relative movement between said machine and a case or the like after completion of the wire binding functions of the machine.

16. Improvements in and relating to wire tying machines comprising wire tensioning, wire twisting and wire cutting devices, a main shaft, direct operative connections between. said devices and said shaft whereby said devices are automatically actuated to tension, twist and cut the wire during a single revolution of said shaft which results in said devices being returned to their normal positions ready to repeat said cycle of operations, a lay shaft, means operable by said lay shaft upon completion of each said cycle of operations to effect movement between the machine and a case that has been bound, power driving mechanism including a constantly rotating driving shaft, a manually operable clutch for coupling said driving shaft to said main shaft, means for automatically tripping said clutch as the main shaft completes a revolution, a clutch for coupling said driving shaft to said lay shaft, means operated by said main shaft as it completes each revolution for actuating said last mentioned clutch to couple said main and lay shafts, and means for automatically tripping said last mentioned clutch after the case moving mechanism has performed its function.

17. Improvements in and relating to wire tying machines as claimed in claim 10 wherein the machine, power driving means therefor, and mechanism for effecting relative movement between the machine and a case or the like that has been bound are mounted upon a tiltable or see-saw frame so that the machine normally assumes a position with its base slightly clear of the case.

18. Improvements in and relating to wire tying machines as claimed in claim 16 wherein the machine, power driving means therefor, and mechanism for effecting relative movement between the machine and a case or the like that has been bound are mounted upon a tiltable or see-saw frame so that the machine normally assumes a position with its base slightly clear of the case.

19. Improvements in and relating to wire tying machines as` claimed in claim 10 wherein the machine, power driving means therefor, and mechanism for effecting relative movement between the machine and a case or the like that has been bound are mounted upon a tiltable or seesaw frame so that the machine normally assumes a position with its base slightly clear of the case. the machine being attached to the front part of the frame and a power unit being mounted upon the rear part of the frame, the frame being pivoted intermediately of its length to a support, and means to counterbalance the frame in a substantially horizontal attitude.

20. VImprovements in and relating to wire tying machines as claimed in claim 16 wherein the machine, power driving means therefor, and mechanism for effecting relative movement between the machine andk a case or the like that has been bound are mounted upon a tiltable or see-saw frame so that the machine normally assumes a position with its base slightly clear of the case, the machine being attached to the front part of the frame, and a power unit being attached to the rear part of the frame, the frame being pivoted intermediately of its length to a support and means to counterbalance the frame in a substantially horizontal attitude.

21. Improvements in and relating to wire tying machines as claimed in claim 15 wherein said support is adjustable vertically upon a stand.

22. In a wire tying machine, the combination claimed in claim 10 and including a lay shaft for actuating said mechanism for moving a case relative to the machine, a constantly rotating power driven, shaft, manually operable means for operatively connecting said main shaft to said power driven shaft so that the main shaft takes the drive for a predetermined period at the expiry of which it is automatically disconnected from the power driven shaft, and means adapted to automatically connect said lay shaft to said power driven shaft at or about the time that said main shaft is disconnected from said power driven shaft, said mechanism for effecting relative movement ben tween the machine and a case comprising an eccentric on said lay shaft, a rod extending from Said eccentric and connected to a pivoted member adapted to engage the rear end of a case and push it forwardly at the completion of binding operations.

23. In a wire tying machine, wire tensioning means comprising a shaft, a pair of opposed cam members mounted to rotate n unison about said shaft while capable of lengthwise movement thereon, means yieldingly opposing lengthwise movement of said cam members in one direction, slide members actuated by rotation of said cam members to move in a straight path lengthwise of the Wire way of the machine, and wire grippers on said slides adapted to grip the wire in substantially horizontal and vertical alignment with said wire Way.

24. In a wire tying machine, the combination claimed in claim 23 and including a rotary wire twisting device driven in synchronism with said cams by a gear train including gears on a lay spindle, and means whereby said twisting device is held against rotation while tensioning is taking place and whereby said slides are held against movement while twisting is taking place.

25. In a wire tying machine, the combination claimed in claim 23 and including wire cutting devices adapted to be actuated in synchronism with said tensioning cams by additional cams rotating with the first mentioned cams.

26. In a wire tying machine comprising wire tensioning, wire twisting and wire cutting devices, a main shaft and operative connections of a direct character, devoid of clutches or other intermediate coupling means, between said shaft and said devices, whereby the latter are, during continuous turning of said shaft in one direction, brought into operation in the sequence named, and by the end of such turning are returned to their original or normal positions ready to repeat the cycle of operations.

H. J. GIBBS., T. A. BINGI-IAM D. W. BINGHAM.

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