US2770183A

US2770183A - Tying machine

Info

Publication number: US2770183A
Application number: US544999A
Authority: US
Inventors: Harris F Hanscom
Original assignee: Hanscom & Co Inc H F
Current assignee: H F Hanscom & Company Inc; Hanscom & Co Inc H F
Priority date: 1955-11-04
Filing date: 1955-11-04
Publication date: 1956-11-13
Anticipated expiration: 1973-11-13

Description

Nov. 13, 1956 Filed Nov. 4, 1955 H. F. HANYSCOM 2,770,183

INVENTOR. Hat/Jr's 1 Hans com ATTORNEYS.

NOV. 13, 1956 HANSCOM 2,770,183

TYING MACHINE mmvrox. zerarrtz's flHa/mc 0/ ATTORNEYS.

Nov. 13, 1956 H. FQHANSCOM 2,770,133

' TYING MACHINE Filed Nov. 4, 1955 G-Sheets-Sheet 5 I I wax/{(1111 4 1 1 al allzal zllll a EYMF.

- INVENTOR. Hal ltz's F5 fiza'ns cam BY I AT TORNEYS.

H. F. HANSCOM TYING MACHINE Nov. 13', 1956 6 Sheets-Sheet 6 Filed Nov. 4, 1955 Fwy mmm

I Q n.

INVENTOR. ,Harr is .5. Hans cam f Y? .4 m

ATTORNEYS.

United States Patent TYING MACHINE Harris F. Hanscom, Barrington, R. I., assignor to H. F. ganscom & Company, Inc., a corporation of Rhode land Application November 4, 1955, Serial No. 544,999

14 Claims. (Cl. 100-10) This invention relates to a tying machine and more particularly to a machine which will wrap binding material about the bundle to be tied and twist the material to hold it securely in place and is a continuation in part of my copending application Serial No. 396,246, filed December 4, 1953.

An object of my invention is to provide a machine which will feed binding material across the object to be wrapped, cut the material to the proper length, and thereafter wrap the bundle and twist the ends of the material to firmly bind the package.

Another object of the invention is to provide a machine for binding articles mechanically instead of manually, thereby saving considerable time.

A further object of the invention is to render the machine semi-automatic so that after placing the article to be tied on a work rest and manually actuating the starting mechanism, the machine will mechanically measure and cut the binding material to the proper length to encircle the article, and draw the binding material around the article, twisting the ends of the binding material together.

Another object of the invention consists in the novel arrangement of cams and switches and the coordination in the operation thereof so that a dwell period is provided to allow the twisting of the binding strip at the completion of wrapping.

A still further object of the invention is to provide a fixed work rest upon which the article to be wrapped may be placed and movable tying arms which wrap the bind-. ing strip around the article by reciprocating away from the work rest.

With these and other objects in view, the invention consists of certain novel features of construction as will be more fully described and particularly pointed out in the appended claims.

In the accompanying drawings:

Figure 1 is an elevational view of the machine with the parts in rest position;

Figure 2 is a side elevational sectional view showing the carriage at the uppermost point of travel;

Figure 3 is a detailed plan view of the slide feed mechanism of the machine;

Figure 4 is a sectional view of the slide mechanism taken on lines 4-4 of Figure 3;

Figure 5 is another sectional view of the slide mechanism taken on lines 5-5 of Figure 3;

Figure 6 is a sectional view of another portion of the,

slide mechanism taken on lines 6-6 of Figure 3;

Figure 7 is a partial detailed plan view of the feeding mechanism after it has passed the disengaging dog;

Figure 8 is a side elevational sectional view of the machine in the second stage of its operation where the binding material is being severed;

Figure 9 is a detailed sectional view of the jaws; a

Figure 10 is a sectional view taken on lines 10-10 of Figure 8 showing the configuration of the bridging mechanism;

tions warrant.

Figure 11 is a detailed sectional view taken on lines 11-11 of Figure 8 showing the manner in which the jaws are pivoted and also the stop mechanism associated therewith to prevent them from turning around their common axis;

Figure 12 is a detailed sectional view of one of the jaws at the upper end thereof showing the slot through which the binding material passes;

Figure 13 is a side elevational sectional view of the machine showing the machine in another stage of its operation where the binding material has been pulled around the article to be tied and just before the jaws have rotated so as to twist the binding material;

Figure 14 is a detailed view of the mechanism used to rotate the jaws wherein the rack utilized to rotate the jaws has been fully loaded by a spring;

Figure 15 is a sectional view taken on lines 15-15 of Figure 13 showing the ratchet loading mechanism associated with the rotating mechanism;

Figure 16 is a rear elevational view of the clutch mechanism showing the solenoid-operated clutch;

Figure 17 is a side elevat ignal view of the driven sprock et associated with the mechanism;

Figure 18 is a detailed sectional view of the latch associated with the rotation of the jaws;

Figure 19 is an electrical schematic diagram of the control switches associated with the solenoid clutch actuating mechanism;

Figure 20 is a perspective view of a bundle of material tied with a binding strip in accordance with my invention;

Figure 21 is a side elevational view of a modified form of mechanism with the parts in rest position; and

Figure 22 is a sectional view taken on line 22 of Figure 21 showing the Geneva motion.

Inproceeding with the invention, I provide a fixed work rest upon which the article to be tied may be placed. Projecting through a slot in this work rest is a pair of jaws that are adapted to pass on either side of the article to be wrapped and which reciprocate relative to the work rest. Associated with the jaws is a feeding mechanism for feeding a binding strip between the two jaws and a rotating mechanism for rotating the jaws about a common axis once they have attained a position below the work rest. A power source is, provided for reciprocating the jaws and associated mechanism to and away from the Work rest and comprises briefly a continuously rotating motor and a solenoid actuated clutch mechanism coupled thereto for periodically clutching and declutching the device as successive opera- In the first embodiment shown in the drawings, the motor through the clutch drives a crank arm which serves to reciprocate the jaws and associated mechanism with reference to the work rest, whilein the second embodiment the motor through the clutch drives a camming mechanism which reciprocates the jaws. Other means familiar to those skilled in the art could be used to raise and lower the jaws and associated mechanism.

Referring now to the drawings which show merely by way of example a first embodiment of the invention, 30 represents the platform which may have legs 31,'the platformserving to mount the tying machine. Two supporting

brackets

32, 33 extend upwardly from the platform 30 and have a cross bridge 34 joining the upper ends thereof, this cross bridge serving to mount one end of a work rest 35, a second bracket 36 serving to mount the other end of the work rest 35'. The work rest 35 has a generally flat upper surface and is provided with a slot 37 therethrough to accept jaws, as will more fully appear hereinafter.

Mounted approximately midway between the

upright brackets

32 and 33 and extending between the platform 39 and the cross bracket 34 is a vertical post 38. Surrounding the post 38 for sliding movement therealong is a linear bushing 39 to which there is attached a transverse member 40/ At one endof the member 4Q a bush-V ing 41 receives the jaw assembly, and at the ether end thereof there is ailixed a bracket 42, which mounts the slide feed mechanism. Extending between the lower end of the bushing 39 and the bracket 36 is a separate transverse member 43 which slidably engages a channel 43 to prevent rotation about the vertical post 38 The parts connected to the bushing 39 just described form a reciprocating carriage which will move relative to the work rest 35 by effecting a sliding movement t thebughijng 39 upon the'post 38. i

To effectthis movement in this instance there is shown a crank arm 44 (Figures 2; and 8 which is pivotally. affixed to the reciprocating carriage and whichis eccentricall-y mounted' byf a pivotpin, 4 5 to a driven sprocket, The sprocket '4 6 is mounted for rotation inbearings that may be received in the support braelret 33 is adapted to be driven in the direction as shown by arrows47' by a chain 48 (Figure 1) that is coupled t9 a driying sprocket 49 on the clutching mechanism (Figure 16) The sprocket 49 is keyed to a shaft SQand has afiixedthereto afsliding clutch member 52. A second clutch member 5 1 freely rotates on the clutch shaft50, theclutch members 5 1 and 52 being held apart by a compression spring 53. The clutch members may be moved together underthe action of a solenoid 54 Whose armature 5 5'is connected by alinkage 56, 57 =and-collar 58-t0 the clutch member 52. Thus, when the armature S5 is drawn in the directionshown by arrow 55A, the lever arm 56 will urge the clutch, member SZ-into engagement with the member 51. Whenthe two clutchmembers Stand 52 are coupled together, this will in effect connect the driving sprocket 49 to the sprocket 59 which is coupled as by a chain drive 60 (Figure 1) to the pinion gear 61 mounted on the shaft of continuously rotating motor M. It will thus be seen that the motor Mis continuously rotating along with the chain drive .60 and the gears 61' and 59. When it is desired to reciprocate the carriage, the solenoid 54 is energized, moving the armature 55 in a direction to couple theoutput: of the motor M through the clutches 51, 52 and gears 49, 46 to move. the cranks arm 44 whichin turn reciprocates'the carriage mounted upon the bushing 39'.

Referring now to Figure 3 Ishow the slide feed mechanism that is affixed to the carriage by means of the bracket 42. This slide feed mechanism generally com; prises abase block 70 into which a longitudinal channel 7- 1 has been cut. Mounted on top of the base block 70 andlongitudinally thereof so as to partially enclose a portion ofthe channel 71; are two ships 72, 72'; The channel 71, therefore, in combination with the strips72, 72 -generally;forrns a guide structure through which the. binding material may be passed; The mechanism for advancing this binding material comprises sliding block 731 having inturned edges 74-, 74 which are adapted to grasp the/lip of

strips

72, 72, respectively. Pivotally. surmounted uponthe block 73 is a feed latch 75 which has a. sharp. portion 76 that passes into the channel-71 soas to press-the bindingimaterial S against the bottom wall of channel 71. The point 76 is urged into engagement bya compression spring 77 -and;may be removed from engagement by a pivoting lever 78; The lever 7 8 is normally inthe positionas shown in Figures 3 and 6; However, as theislide block 73 advances, there is a point in its travel when itwengages a dog 79, this dog 79-striking the lever- 78;a nd movingiit underneaththe nose 80 ofthe feed latch so as to lift the point 76.from the binding strip and thereby discontinue the advancement thereof through the channel 71. Thedog- 79 is adjustable along the longitudig nalextent-of the slide member, and to this end ismounted on a platetbracketsl, a thumb screw adjustment 82 being provided on the dog 79 so that it may b'eplaced' at any desired point to effect the feeding of a proper length of the binding material S. To eifect movement of the member 73 along the slide, there is afiixed to the member 73 a pin 83 which is adapted to slide in slot 84 (Figure 2) in the arm 85. The arm 85 is pivoted as at 86 to the transverse member 40 and has a follower 87 engaging a fixed slotted cam 88 to effect feed of the binding material S.

To insure that the binding material S passes between the two wrapping and twisting jaw arms, a bridging mechanism is pivotally fixed to one end of the, slide feed mechanism. This bridge mechanism comprises a lever arm 90 that is pivoted as at 91 to the base block 70 of the slide mechanism, one end of the lever arm having a channel bridge structure 92 afiixed thereto including depending side walls 92a and 92b, the cross sectional configuration of which is better seen in Figure 10, the lever arm 90 being biased by a tension spring 93 that normally urges it to beiin apositi on across thejaws. The lever arm-9 0,

however, is-provided with a cam lip 94, which is adaptedto engage the fixed upstanding cam post 9 5 In therest position, therefore, of the machine, as shownvin Figure; 1,

thetpoint of contact of this cam 95with the camsurface 94 is above the pivot point 91 of the lever arm 90-and therefore maintains the bri'dge structure in an up position as shownin Figure 1. However, when the carriage. mechanism moves upwardly: to .the position as shown in, Figure 2, thiscampost 95 will thereupon: become disen-- gaged from the cam surface 94, and allow, the tension spring 93,to move the bridge structure downwardly and alntgs t bridge the; gap betweenthe jaws arms. A second cam surface 96 consisting of a roller is also. affixed to thecarn post 95, this cam surface 96 holding the bridge open when the carriage is in: its lowermost position, as is shown in Figure 13, as will more fully hereinafter appear.

A binding strip cutter arm 97 is pivoted on the pivot pin 9;l and carries aknife 98, on one end thereof, the other endcarryingacarn roller 99 As will be seenp-articularly, by referring t9 Figures 8 and 13, this 1cam roller 99 is adapted to engage the inclined surface 75a of the latc'h 75' when the slide 73 moves forward to effect t he pivoting sti n ttb nn llme by e ga h r with: the strip1S, As will be seen by referring to, Figured,

spring arms ltltl normally bias the lever arm 97 in its up ossum;

TQ-QQ QC a wrapping of the binding strip around the article tobe tied, two jaws lltlvand 111v havebeenprovided Thesejawssare provided at their upper endswitlr.

slots

112 and 1 13, which are adapted to receive the bind,-

ing strip as itis advanced from the slide mechanismvde t scribedabove; Figure 12 shows a detailv of the-slot112 nz lt iaw llflwhere e ndi t p 8 s in t a ly pa dt As, will'be seen in .this figure, thi sparticular slot 1 12,has, placed within it-a pivoted lever catch 1 14, which isbiased by compression spring 115 s0 thatthebindingstripas it passe hrpl sh he j w ll remain nd r v g t bittension to prevent the binding material from feeding in: he sv sq i e tiont e l t i nia 11, owe

straight slot of rroper e th o c pt he-end 0 m a r al-i S qw v rr cess ry, it ay barr vided'with' a spring arrangement, as shown 'in Figure '12, 7 so as asra plh; n -c r hec tc ia S asi -tis nasss therein. The jaws 110 and 11 1; are 'pivotally m onnted, on a transversemeniber116, which inturn is fastenedto the end of a vertical shaftv 117. The shaftlll'serves to mount the jawson a commonaxisfor rotationandfis receiveiwithin bearings 41 in the transverse member 40. and seat bearing llSin the transverse member 43.

Each of'the jaw-s 1'10 and,1 1 1pivo,t abont a separate;

axis a, 111a, respectively, and to secureequaljaction each side of the center line between these jaws, 3 561111 circular gear is affixed to the lower end .ofeach 'of;the'

jaws 110 and lllat the pivot axial 10 11 ,and lll'mrespectively, As-willbe seen by referring to Figure 9; the se iserni circular gears 1'19 and 1 2 0 rnesh 'with,e ach other in,

a manner tos ecure equal angular displacement arou d the axes 110a, 111a of the jaws. Urging the two jaws together is a tension spring 121, and fastened to jaw 111 is a cam follower 122, which is adapted to engage a fixed depending strut 123 that furnishes the cam surface. This strut 123 is fixed to the work rest 35 so that when the jaws are in the up position, as shown in Figures 1, 2, 8, and 9, the follower 122 will be engaging this strut 123, thereby keeping the jaws spaced apart as shown, joint spacing action being secured through the action of semicircular'gears 119, 120. However, when the jaws have traveled below the top of the work rest 35, as shown in Figure 13, the cam follower 122 will have become disengaged from the strut 123, thereby allowing the tension spring 121 to pull the jaws together as shown.

When the jaws 111i and 111 have been lowered to the position as shown in Figure 13, the binding strip is in position to be twisted so as to tightly fasten it to the bundle being wrapped. To effect this twisting action of the

jaws

110, 111, the shaft 117 is fitted with a pinion gear 125. This pinion gear 125 is adapted to mesh with a driving gear 126, which is adapted to loosely rotate around its mounting shaft 127. This shaft 127 is spaced from the shaft 117 the distance as shown in Figure 14 and is mounted in bearings that are received in

transverse bars

40 and 43. Ratchet pawls 128 (see Figure are fixed to the gear 126 and are adapted to engage a saw-toothed gear 129 that is keyed to the shaft 127 by key 130. Also aflixed to the shaft 127 is a pinion gear 131 (see Figure 14) which is adapted to engage a rack 132. The rack 132 has a rod 133 affixed thereto that passes through bushings in guide brackets 134, 134', the

guide brackets

134 and 134 being fixed to the transverse member 40 and thereby associated with the carriage mechanism.

At the end of the rod 133 there is affixed a collar 135, and a compression spring 136 extends between the collar 135 and the mounting bracket 134. Mounted ap proximately midway between the brackets 134, 134' on the rod 133 is a cam follower 137 that is adapted to engage the cam surface 138, which is fixed with relation to the mounting plate 30 of the machine by being fastened to bracket 32. It will therefore be seen that as the carriage mechanism moves downwardly, the cam foljlower 137, which is engaging the cam 138,- forces the rod 133 longitudinally so as to compress the spring 136. During this action the rack 132 is rotating the pinion 4 gear 131, which in turn rotates thesaw-toothed gear 129. However, the direction of rotation in this instance is as shown by arrow 139 so that with the ratchet mechanism operating, the gear 126 will not rotate. However, once the cam follower 137 has passed the lower end of the cam track 138, the compression spring 136 through the collar 135 will force the rod 133 in the other direction and the movement of the rack 132 will thereby rot-ate the

gears

127, 126, and 125 in the direction shown by arrow 140 so as to spin the

jaws

110 and 111.

Associated with this mechanism is a locking device to prevent the jaws from rotating during their initial at rest and downward motion periods corresponding to Figures 1, 2, and 8. This mechanism is shown in detail in Figure 18 and comprises a lever catch 150 that is pivoted on a pin 151 that passes through the transverse member 40. One end of this lever catch 150 is biased by a spring 152, while the other end on the other side of the pivot 151 has an extension that is adapted to engage a dog 153 on the rack slide 132. Thus, in the normal rest position, as shown in Figure l, the lever catch 150 is held from pivoting under the action of tension spring 152 by the dog 153, and the upper end thereof thereby engages a rod 154 that extends from the member 116 of the jaw assembly. This prevents the jaw assembly from turning in one direction only. To prevent turning in the opposite direction, a spring catch 155 is aifixed to the far end of the pivot pin 151. This spring catch 155 :is-loosely fitted uponthe pin 151 and is urged against 6 a collar 156 by a compression spring 157 so that the portion may be readily pressed downwardly to al low the passage of the pin 154 to abut with the stop nut 156) mounted on the lever catch 150. It will be noted that as the rack slide 132 moves in one direction under the action of the

cams

137, 138, the dog 153 will allow the tension spring 152 to pull the catch 150 out of the way so that the jaws may freely rotate and the pin 154 will clear the catch 150.

To appreciate the operation of the device, let us first consider the rotation of the. sprocket 46, to which there is attached by means of a pin 45 the crank arm 44 and by which part of the electrical control circuitry is actuated. In Figures 1 and 17 the sprocket 46 is shown in its rest position, and it will be noted that in order to maintain the gear at its rest position and support the weight of the carriage, since the crank arm 44 is exerting a torsional force on the sprocket, a dog 160 is provided, which engages a latch 161 that is provided'with an engaging lip 162 and is pivoted for movement away from the sprocket 46, it being urged toward the gear by compression spring 163. There is an electrical switch A' of the normally closed type which is mounted adjacent the sprocket 46 and which has a follower fa that is adapted to engage a dog 46A so that the switch will be in the open position. A second dog 46b is mounted diametrically opposite the pin 45 so that it will open the switch A when the carriage has reached its maximum down position, as shown in Figure 13. It will thus be seen that when the sprocket 46 is rotated in the direction as shown by arrow 47 (Figure 17), the carriage will first move upwardly to the point where the pivot pin 45 reaches its uppermost position, and then the carriage will start in a downward movement, reaching its lowest point of travel when the pin 45 is at its lowest point and the dog 46b has urged switch A to its open position.

Referring to Figure 19, it will be seen that switch A is in series with the coil 540 of solenoid 54. Thus, its condition controls whether the sprocket 46 will be rotating or not. T0 start the device, however, a foot switch F. S. has been provided in parallel with the switch A to momentarily close it and therebymove the dog 46A from underneath the follower fa. to close switch A. When the sprocket 46 has come around to the position Where the dog 463 contacts the follower fa, it willbe seen that this opens the circuit 'to the solenoid,'thereby stopping the rotation of the sprocket 46. This is to create a dwell in the operation so as to allow the

jaws

116, 111 to spin. Thus, when the cam follower 137 has become disengaged with the cam 133, its rearward movement will actuate switch B which is in the path of the follower 137 (see Figure 13) and switch B will thereby close the circuit to the solenoid coil 54c and the sprocket 46 will rotate, causing the carriage to inove upwardly.

As a safety feature to the electrical control of this device, a separate cut-out switch at the low point of travel of the carriage has been provided. Referring to Figure l, a switch C is shown adjacent the bottom 'plate 30, which has an actuator fc in the path of the lower transverse bar 43. This switch C, as will be seen by referring to Figure 19, is in series with the switch A and thus when the carriage reaches its lowest point of travel, the switch C, which is in the circuit wired for normally closed condition, will be opened, thereby opening the circuit to the solenoid should for any reason the switch A fail to open. This insures that a dwell will occur at the low point of travel of the carriage and continued upward movement ,of the carriage will be conditioned upon the rearward movement of the spinner rac'k mechanism and the engagement of cam follower 137 with the actuator ha of switch B. V i

In order to appreciate. how the various control circuits and mechanical timing circuits are associated with each ing the movement of the rod 133 under the action of the spring 136, that the dog 153 will engage the latch 150 a predetermined instant to limit the rotation of the

jaws

110 and 111, which are twisting under the action of the rack 132. This action of the latch 150 serves as a positive stop for the

jaws

110 and 111 so that they may pass up through the slot 37 in the table 35 and be at a position to complete another cycle.

Figure shows by way of example a completed tied bundle, which in this instance represents a coil of wire 190, which, as will be seen by referring to the part generally designated 200, is slightly compressed under the action of the closing

jaws

110 and 111. The amount of turns of the

jaws

110 and 111 under the action of the rack 132 may be varied at will by changing the gear ratios as well understood. The amount of twist necessary to tie the bundle is determined by the material being used, which in this instance is a binding strip of paper having a reinforcing wire therealong.

In Figure 21 I have shown a modification of my tying machine which is similar in many respects to the embodiment previously disclosed. The main distinction lies in the manner of effecting the various operations above enumerated and particularly the fact that whereas in the previous embodiment the slide feed mechanism was mounted on a carriage along with the vertically reciprocating jaws, the only parts that reciprocate in the present modification are the jaws.

Referring now particularly to Figure 21 wherein like reference numerals, as used in the previous embodiment, have been utilized to the extent applicable herein, represents the platform or base plate upon which the device is mounted. At one end of this platform there is mounted a vertical supporting bracket 30A that is adapted to support the slide mechanism 70, while at the other end of this platform there is a second bracket 36 that serves to mount the work rest 35. In order to obtain rigidity, there is provided a third bracket 308 that ties together the free end of the work rest and the free end of the slide feed mechanism 70. Mounted between the

brackets

30A and 36 is a transverse member 40 which is provided near one end thereof with a bushing 41' to receive the jaw assembly and which also has mounted thereon a pair of spaced vertically extending brackets 32 that serve to support the cam shaft. On the bracket 30A there is mounted a motor M and the clutch mechanism as described in connection with the previous embodiment and which is shown more particularly in Figure 16, the output from this assembly being taken from gear 49 and transmitted to a gear 46 on the-main cam shaft by a drive means 48 which may be in the form of a chain. The slide feed mechanism described in connection with the previous embodiment and which is shown more particularly in Figure 3 is also incorporated in this modification, the description referring thereto being made a part hereof.

The two

jaws

110 and 111 in the present instance are pivotally mounted on a transverse member 116, which is in turn supported on a splined shaft 117'. This shaft is received in a bushing 41 in the transverse member 40' and also in a bushing 118 in the member 30. Keyed -to the shaft 117 and adapted to slide therealong is a pinion gear 131' which is coupled to the output of a'Geneva motion that will be described in more detail. To maintain this pinion gear 131' in a fixed position, two collars 117A and 117B surround the shaft 117' at either side of this pinion gear 131' between the

members

30 and 40. It will be apparent, therefore, that the splined shaft 117' may reciprocate in the bushings 41' and 118' so that gear 131' will remain connected thereto. To limit upward movement of the shaft 117', a shaft collar 230 may be provided.

To effect this vertical reciprocation and to effect the feeding operation of the stock, there is provided a plurality of cams that are mounted upon a camshaft 200. This cam shaft is driven as noted before by a gear 46 i0 fixed thereto and briefly consists of a stock feed earn 206, a bridge cam 212 to control the operation of the bridge 92, a cam 218 to effect the reciprocation of the

jaws

110, 111, and a bevel gear drive 220 which operates the Geneva motion for effecting the twisting operation. The mechanism is shown at top dead center, and for purposes of further discussion it may be well to outline the timing cycle of the cams above referred to.

i From 0-85 degrees the wrapping stock is fed to the proper length as determined by the position of dog 79 and cut off through the action of knife 98. Also duringv this period the bridge 92 is lowered to thread the

jaws

110 and 111 and opens to provide the loop as noted in the previous embodiment, particularly Figure 8 thereof. From degrees to degrees no action occurs. From 90 degrees to 180 degrees of cam motion the arms and 111 are reciprocated downwardly and close through the action of spring 121 and the release of jaw 111 by cam 123A. Between the degrees and 270 degrees of cam motion, the

arms

110 and 111 will remain in the down position, and the Geneva motion will twist the shaft 117' through two or more revolutions, and the stock feed lever will begin to return to the end of its track. Between 270 degrees and 360 degrees the wrapping arms.110 and 111 will move upwardly to the top of their stroke and open under the action of cam surface 123A, and the stock feed lever 85 will complete its return to the position as shown in the drawing.

For ease in explanation, let us first discuss the operation of the stock feed lever 85 under the urgence of its cam 206. It will be noted first that the stock feed lever 85' is pivoted on the shaft 200 and that there is attached thereto remote from the pivot point a linkage assembly made up of links 201 and 202. Link 201 is attached to the stock feed lever 85 at one end, while the other end is pivotally attached to the link arm 202, the free end of the link arm 202 being affixed to the transverse member 40' by a pivoting bracket 203. Along the extent of link;

arm 202 there is affixed a cam follower 204 that is: adapted to ride in a cam groove 205 that is formed in. one of the faces of cam 206. With a rotation of the cam: in the direction of the arrow 47, it will be noted that: the follower 204 is urged to the right as viewed in the: drawing, thus moving lever 85' to the position as shown in dashed lines and designated 85a. move the stock feed slide 73'along the track 70 and perform the same sequence of operations as noted in the previous embodiment and operate the cutting knife 98 at the end of the stroke. It will also be noted that the shape of groove 205 is such as to providean effective dwell of the feed lever arm 85' (see portion 205A), which does: not return until the latter part of the revolution of the cam shaft as noted above.

The bridge 92, the operation of which will now be described, is mounted on a lever arm 90 which is pivoted as at 91 and has an extension remote from said bridge structure onthe other side of said pivot, at which point a camming pin 207 is afi'ixed. A lever arm 208 is pivotally mounted as at 209 on the transverse member 40 and has a forked end 210 which is adapted to engage the pin 207. A cam follower 211 is mounted approximately midway of this lever 208 and engages a cam 212 under the urgence of tension spring 214. This cam 212 has a surface that is generally circular except for a depression 213 during the first part of the rotation thereof which operates the bridge structure as outlined above. It will be apparent, therefore, that as thecarn 212 rotates in'the direction shown by the arrow 47', the follower 211 will enter the depression 213, thus moving lever 208 to'the left as viewed in the drawing and shown in broken lines as at 208A, which action will pivot the lever 90' and drop the bridge as shown in dotted lines as at 92A. The depression 213 is cut on a suflicient sector so that the bridge will remain closed during the feeding operation a sufficient time to allow stock to traverse the

jaws

110, 111

This motion will.

and willrthen immediately begin to raise to form the loop as described in connection with the previous embodiment.

Attached to the shaft 117 is a lever arm 215 which is pivoted i the support 36A as at 216 and which reciprocates the jaws. Approximately midway of this lever 215 there is provided a catn follower 217 which is adapted to engage a cain 218 that has a generally squashed egg shaped outline. Also urging the lever 215 into engagement with this cam as well as urging the wrapping arms 110, Ill upwardly is a spring 219 that is attached to the lever 2 and a suitable datum such as bracket 30B. 7 it will be apparent by referring to the drawings that upon rotation of the cam 213 in the direction as shown by arrow 47' that no movement will occur during the first part of the reason, as the cam surface maintains a perfect circle, However,after passing the 96 degree sector, the cam follower 217 will be positioned downwardly, thus moving the lever 215 and the shaft 217 and it assembly iii a downward direction, dwelling as described above and allowing a return to the top at the end of the cycle.

To effect the rotation of the shaft 117 there has been referred to above a Geneva motion, which is defined in The American Machinists Handbook as a device which gives a positive but intermittent motion to the driven wheel but prevents its moving in either direction without the engagement of the driver, the driver having one or more teeth to allow actuation of any predetermined cycle. In the instant device the Geneva motion is driven from the cam shaft 200 through a pair of bevel gears 2 anda shaft 221. This shaft 221 is coupled to the driver 222 which is provided with one tooth 223 and a cam sector 223'. The Geneva gear sector 224 is made with four slots for the tooth and four circular segments engage the cam 223', which in turn prevents rotation of the gear sector 224 until the driver tooth 223 engages one of the slots such as 225. This Geneva gear is mounted on a shaft 226 and is held in suitable bearings in the transverse members 313 and 49', the shaft 226 additionally having affixed thereto a gear 227 that is adapted to engage the pinion 131. The gear 227 as related to the pinion 131' has the proper gear ratio to. provide the necessary revolution of the shaft 117. In the example given, which requires two revolutions of this shaft, the tooth ratio must be 8 to l to provide the necessary rotation. By suitable excursions of the cam shaft through the above cycle it will be apparent that this. embodiment operates in the same manner as the previous embodiment, except through a different motivati'on.

To actuate this device, a slightly different electrical hook-up would be used, and to that end, there is mounted on the driven sprocket 45' a dog 45A and a microswitch' A such as shown in Figure 17. However, the dog 45B has been eliminated as well as the engaging lever 16% and the electrical hook-up simplified by providing only the switches F. S. and A in parallel, which in turn are inseries with the solenoid 55. Itwill be ap-' placing of the article tobe tied upon the table 35 and the'manual depression of the starting switch F. '8. after" whichthe entire operation of feeding, measuring, cutting, wrapping, and twisting the binding material and the release of the article being tied and the return of the parts to normal position is automatically eifected. ,The only' adjustment that need be made to the operation of the machine would be the length of the binding material to 12 A be supplied, which is dependent upon the size bundle being tied, such adjustment being effected by the'position ofthe's'top dog 79. Ceftain other adjustments are shown in the drawings, for instance, in .the first embodiment the length (if the crank arm 44' may be adjusted to secure the roper operation of the machine when it is assembled, certain variations in manufacturing distances being encountered during the assembly 'ofthe parts of the machine.

I claim: 1. A tying machine comprising a fixed means for supporting the article to be tied, a pair of normally open movable jaws mounted for reciprocation relative to said fixed means, said jaws having means for receiving binding material, means for feeding binding material into said receiving means, means for cutting off a length of the binding material held by said jaws, means reciprocatingsaid jaws away from said fixed means, and means responsive to a predetermined travel of said jaws to rotate said jaws about a common axis thereby twisting the ends of said material.

2. A tying machine as in claim 1 wherein the means reciprocating said jaws is a pivoted lever afiixed thereto and under control of a rotary cam.

3. A tying machine comprising a fixed means for supporting the article to' be tied, a carriage mounted for reciprocation relative to said fixed means, a pair of normally open jaws having receiving means therein mounted upon a common axis and carried by saidcarriage, means including a longitudinal guide for feeding binding material to the receiving means of said open jaws, aknife at the end of said guide for cutting oif said material held in said receiving means, means coupled to said guide to elfect the feeding of saidmaterial between the receiving means in said jaws, means coupled to said carriage to reciprocate said carriage away from said fixed means, and means responsive to a predetermined travel of 'said' carriage to rotate said jaws about their common axis.

4. A tying 'rnachine comprising a fixed meansfor sup porting the article to be tied, a carriage, a pair of normally open movable jaws mounted on a carriage foi" reciprocation relative to said fixed means, said jaws having means for receiving binding material, means mounted on said carriage and reciprocating with said jaws for feeding binding material into said receiving means, means for cutting off a length of the binding material held by said jaws-, means reciprocating said carriage away from said fixed means, and means responsive to a predeter-- mined travelof said carriage to rotate said jaws about a common axisfthereby twisting the ends of said material.

5. A tying machine comprisinga fixed means for supporting the article to be tied, a carriage mounted for reciprocation relative to said fixed means, a pair of normally openjaws having receiving iriean'sd rerein mounted upon a commonaxis and 'ca'rried by said carriage,

means including a longitudinal guide for feeding binding material to the receiving means 'of said open jaws, said guide carried by said carriage, a knife atthee'ndof said guide for cutting off set material heldihsaid receiving means, means coupled to said guide to etfect' the' feeding of said material bs'etween the receiving -means in said jaws, nieanscoupled to' said ca'rri'a'g'e to reciprocate said carriage away from said fixed means, and -ir'ie'a'ns rspo -f s'ive to a predetermined travel or said carriage to rotatesaid jaws about their common axis.

6. A tying machine comprising affixed means for sup- 7 porting the article to be tied, a carriage mounted for reciprocation relative to said fixed means, a pair of normally open jaws havin'greceiving meanstherein mounted upon a common axis and carried by said carriage, means including albngi-tudinal guide for feeding binding material to the receivingineans of said. open jaws, said guide carried by said carriage, a knife at the end of;

said guide for suiting o ff s ai'd mateiial held in said receiving means, bridge means coupled to said guide to guide said material between the receiving means in said jaws, said bridge means having a cam follower thereon, cam means on said fixed means, said cam follower engaging said cam means to lift said bridge means as said carriage reciprocates, said bridge means including means for pulling said material into a loop above the article to be tied, said knife means responsive to movement of said jaws to cut said material as said jaws reciprocate away from said fixed means, and means responsive to a predetermined travel of said jaws to rotate said jaws about a common axis.

7. A tying machine comprising a fixed means for supporting the article to be tied, a carriage mounted for reciprocation relative to said fixed means, a pair of normally open jaws having receiving means therein mounted upon a common axis and carried by said carriage, means including a longitudinal guide for feeding binding material to the receiving means of said open jaws, said guide carried by said carriage, a knife at the end of said guide for cutting off said material held in said receiving means, a crank arm coupled to a source of power and to said carriage for reciprocating said carriage, and means including an arm responsive to the reciprocation of said carriage coupled to a portion of said feeding means, the reciprocation of said carriage advancing said material through the receiving means in said jaws, said jaws being rotatable about said common axis w reby the article may be tied.

8. A tying machine as in claim 7 wherein means for rotating said jaws about their common axis have been provided, said means being responsive to a predetermined travel of said carriage.

9. A tying machine as in claim 7 wherein a ratchet gear is coupled to a shaft on the common axis of said jaws, a rack, said gear being engaged by a rack, a spring coupled to said rack, means for stressing said spring as said carriage reciprocates away from said fixed means, and means responsive to a predetermined travel of said carriage to release the stress on said spring, thereby rotating said jaws.

10. A tying machine comprising a vertical reciprocating carriage and a fixed work rest, a pair of normally open jaws carried by said carriage, means for rotating said jaws about a common axis, means associated with said carriage for feeding binding material to said jaws and over a bundle placed on said work rest, means cutting off a length of binding material held by said jaws, electrically operated means governing the reciprocation of said carriage toward and away from said work rest to draw the binding material around said bundle as said carriage and jaws move away from said work rest, first switch means in circuit with said electrical means, said switch means responsive to the maximum travel of said carriage to open said circuit and provide a dwell to allow said jaws to rotate, second switch means in parallel with said first switch means, said second switch means responsive to the rotation of said jaws to close the circuit to said electrical means, thereby reversing the travel of said carriage and ejecting said bundle by the upward movement of said carriage.

11. A tying machine as in claim 10 including latch means to limit the rotation of said jaws, said latch means aligning said jaws with said feeding means.

12. A tying machine as in claim 10 wherein said feeding means comprises a guide channel in which binding material is disposed, a feed latch adapted for sliding movement along said channel and having a portion thereof engaging the binding material in said channel, an arm adapted to lift said latch from engagement with said material, a first dog at the end of said channel urging said arm away from said latch, and a second dog adjustable along said channel to engage said arm with said latch lifting said latch away from said material.

13. A tying machine as in claim 12 wherein said feed latch is provided with a cam surface and said means cutting off the binding material includes a cam follower adapted to be engaged by said feed latch cam surface.

14. A tying machine comprising a fixed work rest, a pair of normally open jaws mounted for vertical reciprocation on a rotary shaft, means for feeding binding material to said jaws and over a bundle placed on said work rest, means cutting off a length of binding material held by said jaws, a first cam and a cam shaft therefor, an arm coupled to said jaws and having a follower engaging said cam, said arm reciprocating said jaws toward and away from said work rest to draw the binding material fed between said jaws around said bundle as said jaws move away from said work rest, 2. Geneva motion having its input coupled to said cam shaft, the output of said Geneva motion coupled to said rotary shaft, the gear train of said motion being arranged so as to rotate said jaws at the maximum travel thereof, and switch means coupled to said first cam to stop the travel of said jaws when they have moved to their maximum excursion above said work rest.

References Cited in the file of this patent UNITED STATES PATENTS 1,261,589 Mogan et a1. Apr. 2, 1918 2,524,316 Jackson Oct. 3, 1950 2,742,851 Fryer Apr. 24, 1956