US2363391A - Tying machine - Google Patents

Description

NOV. 21, 1944. BUNN 2,363,391

TYING MACHINE Filed July 16, 1942 8 Sheets-Sheet 2 Nov. 94 B. H. BUNN 2,363,391

TYING MACHINE Filed July 16, 1942 a Sheets-Sheet s Nov. 21, 1 944. B. H. BUNN 2,363,391

TYING MACHINE Filed July 16, 1942 8 Sheets-Sheet 4 dmw.

. 21, 1944- EH. UNN 2,363,391

TYING MACHINE Filed July 16, 1942 8 Sheets-Sheet. 6

NOV. 21, 1944. B, H, N 2,363,391

TYING MACHINE Filed July 16, 1942 8 Sheets-Sheet 7 J emz Nov. 21, 1944. B. H. BUNN TYING MACHINE Filed July 16, 1942 8 Sheets-Sheet 8 Patented Nov. 21, 1944 TYING MACHINE Benjamin H. Bunn, Chicago, 111., assignor to B. B. Bunn Company, Chicago, 111., a corporation of Illinois Application July 16. 1942. Serial No. 452,115 21 Claims. '(01. 100-31) My invention relates to machines which wrap twine about packages, and secure the ends of the twine wraps together, as by tying. More especially it concerns a type of package wrapping machine known to those familiar with the art as a needle arm machine. In the needle arm type of package wrapping and tying machine the arm which lays or wraps the twine about a package does not pass around the package as does the crank end of a crank type wrapping arm, but instead has more of a reciprocating motion.

My Patent No. 2,274,526, issued February 24, 1942, shows a needle arm machine, as does likewise my patent application, Serial No. 424,388, filed December 26, 1941. Both the above patent and the application show machines in which a reach of twine is held to extend vertically upward from a package support table, so that a package to be tied may be.pushed against the reach to deflect it, and thereby form a bight partially surrounding the package, so that when the twine arm, or needle arm as it is called, descends, it will close the bight thus formed to complete a wrap of twine about the package. The ends of the wrap of twine are then secured together as by knotting, and the end of the twine wrap connected to a twine supply is severed and the package released. y

The twine knotting and severing mechanism employed in the illustrative embodiment of my present invention is in general similar to that shown in my patents, Nos. 1,606,290 of November 9, 1926, and 1,994,453, of March 19, 1935, and the reader is referred to those patents for a full understanding of such mechanism.

In my present invention I prefer not to have the reach of twine held vertically by the needle arm at the initial, or at rest, position of the machine, but rather to have a reach of twine held horizontally beneath the table, so that a package to be wrapped will lie above such reach of twine. This arrangement permits a package to be inserted into wrapping position in the machine without having to push it against a vertical reach of twine to form a bight therein. It also permits a package to be fed in from the side, which may be desirable in some cases where a conveyor is used to feed packages to the machine for wrapping and tying.

The entire wrapping operation, followed by the subsequent automatic ejection of the wrapped package, is accomplished by a new orbital arrangement, which in-some respects achieves advantages of the crank arm type, while at the same time retaining other advantages peculiar to the needle arm machines.

This new orbital arrangement follows a modified rectangular path, and is accomplished by moving the twine laying end of the needle arm first upwardly and then forwardly over the rear side and top of a package positioned in the machine over the initial horizontal reach of twine beneath the table. The twine is then carried downwardly across the front side of the package to complete the wrap, and, as it approaches the knotting position, is swung sharply rearwardly to hook the twine into a twine catcher associated with the knotter. The twine laying mechanism dwells at this point during the knotting and twine severing operations and then moves rearwardly to lay the next reach of twine beneath the table. The same movement of the twine laying mechanism which lays this next reach of twine beneath the table is utilized to carry the wrapped package rearwardly to eject it from the machine.

My present invention is particularly useful for rapidly wrapping packages which may be produced by automatic or semi-automatic machines, and may be arranged automatically to receive, position, wrap, and eject successive packages with no further attention than an initial adjustment for package size, and the replenishing of the twine supply when it is exhausted.

The machine may be adjusted rapidly and easily for a particular size of package, and when so adjusted insures maximum effectiveness and efflciency of movement. While lacking the universality of some of my other tying machines, the present type of machine is thus better suited for performing its own special job.

The packages are adapted to initiate, automatically, the wrapping and tying cycle as they are moved into tying position, and the completion of each tying cycle may cause the feeding of the next package into tying position, so as to provide for continuous operation as long as there are packages remaining to be tied. The machine set forth in the following description and the accompanying drawings. 7

In the drawings, of which there are eight sheets:

Fig. 1 is a view in perspective of a package wrapping and tying machine made in accordance with the present invention;

Fig. 2 is a view in front elevation of the machine of Fig. 1 with portions of a casing, and of a transverse frame member, broken away to show the operative features of the machine;

Fig. 3 is an enlarged fragmentary section taken in the plane of the line 3- -3 of Fig. 2;

Fig. 4 is a section taken'in the plane of the line 4-4 of Fig. 2, an upper guard member being omitted;

Figs. 5 to 8, inclusive, are more or less diagrammatic views showing four successive stages of a wrapping cycle of the needle arm orbital operating mechanism;

Fig. 9 is an enlarged fragmentary section taken on the plane of the line 99 of Fig. 2;

Fig. '10 is a similar section taken on the plane of the line Ill-l of Fig. 2;

Fig. 11 is a further enlarged fragmentary section taken on the plane of the line Hll of Fig. 4;

Figs. 12 and 13 are enlarged fragmentary sections taken as on the plane of the line i2|2 of Fig. 4, showing respectively the engaged and the released positions of a safety break-away device for the needle arm;

Fig. 14 is a similar section taken on the plane of the line M-M of Fig. 4 with the break-away device in engaged position;

Fig. 15 is an enlarged fragmentary section taken on the plane of the line |-I5 of Fig.2, showing the rocking arrangement for the twine laying, or needle arm, the arm being shown in normal position in solid lines, and in rocked position in dotted lines;

Fig. 16 is an enlarged fragmentary detailed section taken on the plane of the line 16-46 of Fig. 4;

Fig. 17 is a similar section taken on the plane of the line l1-l1 of Fig. 4;

Fig. 18 is a similar section taken on the plane of the line I8-I 8 of Fig. 4; and

Fig. 19 is an enlarged, fragmentary section of a modified arrangement showing an automatic package feed mechanism, which section is taken as on the plane of the line 9--9 of Fig. 2. For

the purpose of simplicity this package feed mechanism has been omitted from the other views of the drawings.

Fig. 20 is an enlarged sectional detail view taken in substantially the vertical front-to-rear median plane through the temporary hold-down clamp structure of the present machine.

Referring to the drawings in detail, a frame 3| comprises end frame members 32 and 33 which may be of cast iron, with front and rear side plates 34 and 35 rigidly connecting the end frames together. Swivelled casters 36 may be provided to facilitate spotting a machine in a desired location.

A table top 31, which may be of sheet metal, is mounted on top of the frame, and has an elongated slotted opening 38 therein in which the ,needle arm and package feeding mechanism, to

be described later herein, are adapted to operate. In the illustrated embodiment of the machine this opening extends inwardly from the forward edge of the table top in the form of an elongated notch, as best illustrated in Fig. 1.

A cabinet or enclosure II is assembled from four sub-assembled panels to enclose the principal operative parts of the machine to protect the parts from damage and also to act as safety guards to prevent injury to employees and operator. The panels comprising the cabinet are supported on brackets such as the brackets 40 and 43 of Fig. 2, and a hood 44 is provided to shield a needle arm carriage and associated parts as an additional safety feature.

Suitable inspection and access doors 4! preferably areprovided inthe front and right hand sides respectively of the cabinet to facilitate inspection and adiustment of the operative parts of the machine.

A number of operative parts of the present machine are similar to those of my Patent No. 1,606,290, and for the purpose of simplifying the present description, such'parts, which include the twine knotting and severing mechanism and other operating parts will be referred to briefly before progressing to adescription of the novel features of my present invention.

A motor 46 is mounted on a motor support plate 41 secured to the frame, the motor having speed reducing drive connection, as by means of a V-belt, with a clutch pulley 48 which is journaled on a shaft 49. Theshaft 49 is journaled in the frame, and the clutch pulley 48 is adapted to have driving connection as by means of a clutch 50 with the shaft 49.

The clutch is operated by a clutch lever 63 in a manner similar to that of my Patent No. 1,606,290, by means of a clutch actuating mechanism which will be specifically described later in the present specification.

The clutch 49 has a pinion i4 keyed thereto, the pinion being in continuous driving engagement with a central unmutilated, or continuously toothed, portion of a mutilated gear 65. The mutilated gear is keyed to a cam shaft 56, also journaled in the frame.

The cam shaft has the main cam block 5? keyed thereto, and is arranged to operate the twine knotting and severing, and clutch control mechanism in' a manner similar to that of my Patent No. 1,606,290.

The mutilated gear in the illustrated embodiment of my present invention is mutilated on both sides, instead of on one side Only as in my Patent No. 1,606,290. The purpose of this dual mutilation will be brought out later when describing the novel features of my present invention.

A twine supply bucket 58 is mounted on a bracket 59 carried by the frame, and is adapted to receive and support a supply of twine 60. The twine is adapted to feed from the supply in the bucket, through an eyelet 63 in the supporting bracket, and thence through an eyelet in a bracket 64 mounted on the end frame member 33. From here the twine is carried upwardly and through an adjustable spring controlled twine tensioning device 65, from whence it is carried laterally, as illustrated in Fig. 2, and. is led downwardly through a twine guide eyelet 6B in the,

95 and the crank 94 is provided by a machine movement of the twine laying end of the needle arm is accomplished by a combination of successive vertical and horizontal motions, the horizontal components of which are accomplished by a reciprocating carriage 89, and the vertical components of which are accomplished by a vertically reciprocating rod I which is slidably mounted in bearings on the carriage.

The carriage 99 is illustrated best in Figs. 2 and 4, the upper portion only of the carriage being visible in Fig. l. The carriage is mounted on a horizontal rail 18 of rectangular cross section. which is supported on brackets I4 bolted to the outside of the u per end of the end frame member 03. The body of the carriage preferably is of cast iron, and has four ball bearing rollers 18 mounted one at each of the four corners of the main body portion 15 of the carriage, which body portion is in the form of a vertically disposed rectangular plate. The rollers are mounted to engage the top and the bottom of the rail I3 rather closely so as to avoid undue vertical movement of the carriage under the vertical reciprocating and other stresses to which it is subjected in use.

A pair of retaining flan es I1 and 18 in the form of metal strips are bolted in place to engage the opposite side of the rail from that adjacent the body 15 of the carriage, to secure the carriage against lateral displacement from the rail.

A bracket I9 extending outwardly from the carriage supports a vertically disposed bearing at the forward end of the carriage, this forward bracket being well illustrated in .Figs. 1 and 2. A

pair of vertically separated and aligned larger bearings 80 and 83 are supported on a second bracket 84 at the rear of the carriage, this second bracket and its pair of vertically separated bearings being illustrated best in Fig. 4. These brackets and bearings may be cast integrally with embodiment illustrated having this ost located at a mid-point thereof. and a threaded connecting rod 89 is threaded into an opening in this post 88. The other end of the connecting rod is threaded into a collar 90 which is pivoted on a T- bolt 93 adjustably mounted on a crank 94 which is journaled on the outer end of the main cam shaft 56. Some of the specific features, and the method of adjustment. of the crank and connecting rod are omitted from this phase of the description. so as to describe first the general operating characteristics of the carriage reciprocating mechanism.

The mounting of the crank 94 and a chain drive sprocket 95 therefor is illustrated in section in Fig. 11. The crank 94 is mounted on the hub of the chain sprocket 95, which in turn is journaled on a bushing 96. The bushing 96 is mounted in a bearing in the end frame member 33, in which the main cam shaft 58 is journaled. A washer 9! is seated in a recess in the outer end of the sprocket hub, the washer being secured to the end of the cam shaft by a machine screw 98. Shearpin driving connection between the chain sprocket Ill) screw 98-, which penetrates the sprocket and is threaded into the hub of the crank.

The sprocket and its connected crank have driven connection, by means of a chain I00, with a driving sprocket I03 which is keyed to a short shaft I04, joumaled in the frame, and having a drive pinion I05 keyed thereto in a position to engage the interrupted left hand toothed portions of the mutilated gear as it appears in Fig. 2.

This drive pinion I05, and the associated teeth on the mutilated gear 55 for driving it, are illustrated in Fig. 10. The drive pinion I05 is provided with a shoe I08 secured to a side thereof by screws I01. which shoe is adapted to ride onto laterally extending flanges I00 and I09. These flanges are provided coextensively with the mutilated or untoothed portions of the mutilated gear in the path of the pinion I05 so as t hold the pinion against turning, i. e., in the position illustrated in Fig. 10, during the entire time when the pinion is over either of these mutilated portions of the mutilated gear.

Each of the unmutilated portions of the mutilated gear in the path of this pinion is of a length to cause one complete rotation of the pinion during each of the two periods, in the cycle of rotation of the mutilated gear, in which the pinion is engaged by the teeth of the unmutilated portion of this side of the gear. The driving sprocket I00. however, which is keyed to the same shaft as the pinion I05, has but half the number of teeth of its driven sprocket 95. Therefore, for each complete rotation of the pinion I05 the sprocket and its associated crank 94, will rotate but one half revolution. The pinion I05 illustrated in Fig. 10 is arranged to hold the crank 94 either in the position illustrated in-Flg. 4, or from this position, when the pinion is over either of the untoothed portions of its side of the mutilated gear. Thus, for each rotation of the pinion 95. which occurs twice during the cycle of the mutilated gear, the carriage will be moved throughout its maximum effective length of travel as determined by the adjustment of the connecting rod 89.

With respect to the more specific features and adjustments of the connecting rod 89, reference is made to Figs. 4, l1, l6, l7 and 18. The crank 94 has an undercut recess IIO (see Fig. 17) in which the head I I3 of the T-bolt 93 is slidably inserted. A bushing H4 is mounted over the stem of the T-bolt, and on this bushing the collar 90 is jcurnaled. A retaining nut H5 is provided on the threaded end of the T-bolt, and is turned down against the end of the bushing to secure the bushing H4 in adjusted position on the crank. The collar is of less width than the length of the sleeve of the bushing, so that the nut does not clamp the collar 90 against rotation on the bushing.

The collar 90 is provided with a threaded opening IIG therein to receive the threaded end of the connecting rod 89, which on this end, is threaded with a single thread.

The extreme left-hand end portion of the connecting rod 89, as illustrated in Fig. 4, is reduced in diameter below the roots of the threads (see Fig. 16), and a weighted blade II! is pivoted on this reduced portion. The weighted blade in retained in position on the reduced portion by a cap II8, which is pinned to the connecting rod, and is provided with a rectangular boss H9 projecting axially therefrom whereby the connecting rod may be rotated for adjusting the stroke of the carriage, by means of a socket wrench, not shown.

An opening I20 (see Fig- 1) is provided in the cabinet in longitudinal alignment with the connecting rod in its normal, or at rest, position, so that the wrench may be inserted through this opening, and may be manipulated from a point outside the casing.

The weighted blade member I" has an upwardly projecting narrow blade portion I23 which is adapted to fit in a notch I24 in the hub of the crank 94. It also has a weighted lower portion I22 which normally holds the blade portion vertical and laterally beyond the plane of rotation of the crank. When adjusting the stroke of the carriage however, the blade portion I23 is swung manually into the notch I24 in the crank hub, and is held there until the adjustment of the stroke, by turning the threaded connecting rod, is completed.

The blade serves as an anchor during such adjustment to retain the connecting rod against endwise movement. This anchoring of the connecting rod, and the features and functions of the stroke-adjusting mechanism about to be described, are designed to maintain the position of the carriage at the end of its forward stroke constant with respect to the twine'knotting and severing mechanisms, the locations of which are fixed with respect to the frame. This is necessary because the knotting and severing operations are performed with the carriage in its fully forward position.

The pivoted post 88, illustrated in Fig. 18, has

a reduced axially projecting portion I25 which is pivoted in an opening in the lever 86, and is held in position within this opening by means of a retaining washer I26 and machine screw I2I. An opening I3I through the post 88, at right angles to the axis of the post, is double threaded to receive the rear end of the connecting rod, which is threaded with a similar double thread with double the pitch of the single thread on the forward end thereof.

The connecting rod may be locked against rotation in this opening by means of a thumb screw I28 which engages a lockin plug I29. The plug may be of semi-soft metal, such as brass, so as not to damage the threads of the connecting rod against which it is pressed by the thumb screw. The plug I29 is freely insertible in the thumb screw opening, and may have the inner end thereof which engages the threads of the connecting rod serrated to conform to the threads. 1

To increase the length of stroke of the carriage, and co-incidentally to move rearward its normal or at rest position, the thumb screw I28 is unscrewed sufliciently to relieve the pressure from the plug I23. This frees the connecting rod for rotation. The retaining nut II then may be partially unscrewed from the threaded end of the T-bolt 33, which releases the bushing and frees the T-bolt for slidable movement along the un-" dercut recess in the crank 34.

The'weighted blade I" then is swung in a counterclockwise direction from the position illustrated in Fig. 16 so that the blade portion I23 are both either right or left hand threads; and, as already mentioned, the double thread has double the pitch of the single thread.

The adjustment must be made with the crank in the position illustrated in Fig. 4, because of the location of the notch I24.

In order to visualize this adjustment, let us assume that the threads on both ends of the connecting rod are right hand pitch, and that we desire to shorten the stroke of the carriage by a distance equal to two thread pitch lengths. First the thumb screw I28 and the knurled nut I I5 both are loosened to release the connectin rod for free rotation, and the T-bolt 93 and its associated parts for slidable movement lengthwise of the slot in the crank 84. The weighted blade is held manually in the notch I24 to prevent endwise movement of the connecting rod during adjustment.

The socket wrench, is fitted over the boss M9 on the end of the connecting rod 89, and the connecting rod is rotated one complete revolution to the right. This rotation, by the action of the single right hand thread of the connecting rod on the collar 30. draws the T-bolt along the slot I III in the crank 94 a distance equal to the pitch length of a single thread toward the hub of the crank. Simultaneously it draws the pivoted post 88, by means of the double thread, double the distance of the single thread pitch length in the same direction. The assumed adjustment now being completed the socket wrench is removed, the thumb screw I28 and knurled nut IE5 are tightened to secure the connecting rod against rotation and the T-bolt against displacement, and the weighted blade I" is released to permit its weighted lower end I22 to swing the blade 523 free of the notch I24 and beyond the plane of the crank 34.

This adjustment shortens the throw of the T-bolt and its associated parts during a rotation of the crank 94 by a distance equal to two thread pitch lengths (one on each side of the crank axis) but it also advances the starting, or at rest, posttion of the post 80 relatively to the same crank axis by two such thread lengths. Therefore, the position of the post 88 when the crank is swung 180 from its starting position (i. e., its position of dwell for the twine knotting and severing opopposite direction from that just assumed will enters the notch I24 in the hub of the crank 94.

This anchors the connecting rod against endwise movement during the adjustment of the stroke length, without interfering with its free rotatability. The connecting rod 89 may be rotated by increase the stroke proportionately, and likewise will change proportionately the normal or at rest position of the post 88, and its connected lever 86 and carriage 69.

A cross head I30, which may be of cast metal, has a pair of rods comprising the reciprocating rod 10, and a smaller guide rod I33 mounted in boxes I34 cast integrally with the cross head. These rods are mounted for vertical slidable movement in the bearings on the carriage.

Thesmaller guide rod I33 extends downwardly a distance somewhat greater than the maximum length of vertical stroke of which the cross head I30 is capable, while the larger reciprocating rod I0, which is connected to the vertical reciprocating drive mechanism, extends downward a. greater distance, and is provided with a break-away fitting-l35 onits lower end. This fitting has releasable, hooked, sliding engagement with a rectangular rail I36, which is pivotally supported on the ends of a pair of cranks I31 and I38 of equal length.

The cranks are keyed to short forward and rearward shafts I39 and I40, respectively, journaled in the frame. A pair of chain sprockets I43 and I44 (see Fig. 4) are keyed to the shafts I39 and I40, and are engaged by a drive chain I45 whereby the cranks are driven in synchro- I48 mounted on a side thereof and positioned to engage, respectively, laterally extending flanges I49 and I50, which are provided opposite the untoothed portions of the mutilated gear in the path of the pinion I46. The two toothed portions of the mutilated gear in the path of this pinion, each of which is of a length to rotate the pinion through an arc of 180, are located to cause these two semi-rotations of the pinion I46 to occur at proper stages of the operative cycle of the mechanism.

The needle arm 62 as illustrated in Figs. 1, 2, 3 and 4 comprises a straight rod-like portion I53 pivoted horizontally in the cross head I30, the outer or left hand portion of the needle arm, as illustrated in Fig. 2, being bent downwardly at right angles, and having a hook shaped lower portion with the extreme lower end thereof bent to extend horizontally, and provided with the horizontal twine receiving opening 61 therein. This horizontal portion terminates in the same vertical fore and aft plane as the twine catcher 68, so that as the needle arm passes around the twine catcher in each cycle of its operation, it will lay the twine into the twine catcher in position for completion of the knotting operation as described in my Patent No. 1,606,290.

A lever arm I54 is secured to the right hand end of the horizontal portion of the pivoted needle arm as illustrated in Figs. 1 and 2, and also is shown in Figs. 4 to 8 and 15. The lever arm is positioned to engage a roller I55 pivoted on an extension of the carriage as the cross head I30 is moved to its lowermost position by the vertically reciprocating mechanism.

The lever arm I54 is provided with a recess I56 in its upper edge in which is seated the rounded head of a pin I51 which holds in compression a coil spring I58. The upper end of the spring I58 is engaged by an adjusting screw I59, which in turn is locked in adjusted position by a lock nut I50.

The solid line illustration in Fig. shows the needle arm as it would appear slightly above the lowermost point in its downward movement, at the forward end of its orbit, and with the lever arm I54 just engaging th roller I65. In this position it will be noted that the lower end of the needle arm is positioned forwardl of the twine catcher 58. In the dot and dash line illustration of Fig. 15 the parts have reached their lowermost position, and the lever arm I54 and its connected needle arm 82 have been swung in a counterclockwise direction to the dot and dash line position of Fig. 15, to swing the twine into engaged position in the twine catcher.

A package stop bar I5I is secured in vertical position on the front of the cross head I to act as a package stop when inserting a fresh package into wrapping position in the machine, and a pair of vertical package ejector bars I62 are Provided on the back of the cross head to push each wrapped package rearwardly and eject it from wrapping position after completion of the wrapping operation.

The entire orbital movement of the twine laying end of the needle arm can be followed in the diagrammatic illustrations of Figs. 5 to 8, inclusive, the path of this twine laying needle end being shown in dot and dash lines in these figures. In Fig. 5 the dotted line illustrations of the cranks I31 and I38 and the rail I39, together with the vertically reciprocating portions of the mechanism, indicate the normal, or at rest, positions of these parts. In the solid line illustration of Fig. 5 the cranks I31 and I38 have moved through an arc of in the direction of the arrow from this normal position. The twine laying lower end of the needle arm has moved upwardly, and has been swung slightly forwardly along the curved dot-and-dash line from its lowermost, rearward position.

This forward component of its movement in Fig. 5 is caused by the raising of the lever arm I54 from the roller I55 which permits the spring I58 to swing the lever arm and its connected needle arm 62 in a clockwise direction to the position of Fig. 5. The crank 94 has not yet begun to rotate in the illustration of Fig. 5.

In Fig. 6 the cranks I31 and I38 are in their uppermost positions, and the crank 94 has reached its first half rotation so that the carriage has now moved to its extreme leftward position, and the cranks I31 and I38 are ready to start the slide rail I36 and its associated parts on their downward travel.

In Fig. 7 the carriage is still in its extreme forward position,and the slide rail I38 has moved the vertically reciprocating parts of the cross head to their lowermost position. The lever arm I54 has engaged the roller I55 pivotally to move the needle arm in a counterclockwise direction to swing the twine into the twine catcher to be engaged thereby as shown in dot and dash lines in Fig. 15. The parts dwell in the position illustrated in Fig. '7 during the knotting and severing operations on the twine.

It is important, in adjusting the length of stroke of the carriage, that sufficient clearance be provided at the forward end of the stroke to insure the ejector bars I62 clearing the front of the package when moving from the position of Fig. 6 to that of Fig. 7. This brings the ejector bars in front of the package ready to push it rearwardly upon the final rearward movement of the carriage.

Fig. 8 illustrates the parts moving toward the final or at rest position toward the end of the cycle, which will be reached when the crank 94 swings through another approximately 60 of counterclockwise rotation, to bring this crank to the position illustrated in Fig. 5. This last portion of the cycle moves the carriage and its associated parts to their extreme right hand positions. During this latter phase of the cycle illustrated in Fig. 8 the knotting' and severing operations have been completed, the tied package is being ejected by the ejector bars I62, and a new package, not illustrated in these views, is being drawn into wrapping position in the machine. When the crank 94 completes its cycle and reaches the position illustrated in Fig. 5, the main cam block 51 will have completed a cycle, and will have returned to the position of Fig. 3. Upon reaching this position, if the clutch release mechanism is in its normalposition as illustrated in Fig. 3 the side ,cam I98 will force the slip link I95 outwardly against the roller I 91 and move the clutch lever 53 to clutch releasing position.

A temporary package clamp (see Figs. 1, 2 and 3) is provided near the outer end of the cross head I30 and comprises a forwardly facing metal strip I63 pivotally mounted in a vertical plane on the cross head as at I69 (Fig. 20) and having a roller I64 mounted to extend laterally from its lower end. An angle clamp I65, including a forwardly extending leg and an upwardly extending leg, has its upwardly extending leg secured to a bracket I66 by which the angle clamp is slidably mounted for vertical adjustment on the upper portion of the strip member I63, with the back of the upwardly extending clamp leg opposing the front face of the strip member. The bracket I66 extends rearwardly beyond the opposite edges of the associated portion of the strip member I68 and is provided with a readily manipulable clamp including a fixed block I61 which opposes the rear face of the strip member I63. The manipulable clamp is operated by a pointed tip screw I61 which is threaded into the top of the block I61 and extends upwardly a suflicient distance so that its head can be engaged above the upper end of the strip member I63. The point of the screw I61 cams against and drives a. clamp ball I61 out of an opening I61 in the forward face of the block I61 into frictional engagement with the rear face of the strip I63, thereby drawing the upwardly extending leg of the angle clamp member I65 against the front face of the strip member, thus to lock the angle clamp I65 in the preferred vertically adjusted position on the-strip member I63. Release of the clamp I61, I61 for eiiecting readjustment of the clamp member I65 is accomplished simply by loosening the screw I61- to release the ball I61, and then moving the angle clamp I65 to the position desired 0n the 40 strip member I63, whereupon the adjusted position is maintained by turning the screw I61 tight again.

This angle clamp is adjusted to engage a package temporarily when the package is moved into wrapping position in the machine, as illustrated in Figs. 3 and 19, until the main clamping mechanism is brought into engagement with the package by the operation of the wrapping mechanism. The roller I64 on the lower end of the strip member is positioned to engage a. clutch operating mechanism comprising a T member I68 formed of two metal strips I69 and I10, see Fig. 3, riveted together as at I13, and pivoted by two screws I14 and I15 to a pair of parallel links I16 and I11. These links in turn are pivoted on a vertical bracket member I18 secured to the frame. The upper parallel link I16 extends outwardly beyond the stem of the T, and has an adjustable, two-part, link I19 pivotally connected to the outer or free end thereof. The upper portion I80 of the two-part link I19 is secured for longitudinal adjustment to a lower portion I83 by means of a bolt I84, which is mounted in a slotted opening in the lower portion I83. By releasing the bolt and moving the portions I80 and I83 relatively to each other, the effective length of the composite link may be adjusted.

The lower end of the composite link I19 is pivoted to the end of an arm I85 of a bell crank lever I86. The bell crank lever in turn is pivoted on a bracket I81 mounted on the frame. A coil spring I88 is connected between the arm I85 of the bell crank lever, and a pin I89 mounted in the frame-supported bracket I18, normally to urge the bell crank lever in a clockwise direction about its pivot, as shown in Fig. 3, thereby raising the head of the T to its maximum upward position.

A counterweight I is threaded onto a stem I93 carried by the bell crank lever to assist the action of the coil spring I88, and to add mass to the moving parts of the clutch operating mechanism. The weight I90 is retained in adjusted position on the screw by means of a set screw I94.

A slip link I95 is pivotally connected to a lower arm I96 of the bell crank lever, and normally is positioned between a roller I91 on the upper end of the clutch lever 53 and a side cam I98 mounted on the cam block 51. This portion of the clutch operating mechanism, from the bell crank lever to the clutch lever, is similar to that described in my Patent No. 1,606,290, and therefore will not be described in further detail here.

The operation of this temporary package clamp and clutch operating mechanism is clearly apparent from Figs. 3 and 19. When a package I99, indicated in dotted lines, is pushed into package tying position, as is the center package in Fig. 19, it engages the strip member l69, moving the strip member in a counterclockwise direction, and bringing the angle clamp I65 down on top of the package to hold it in position. At the same time this swings the roller I64 downwardly, depressing the T member I68 and swinging the left hand ends of the parallel links I16 and I11 downwardly. This forces the composite link I19 downwardly, and swings the bell crank lever I86 counterclockwise against the action of the coil spring I88 and the counterweight l90. This action withdraws the slip link I95 to release the spring pressed clutch control lever 53 and thus to initiate a wrapping and tying cycle of the mechanism. The slip link I95, clutch operating lever 53, and side cam I98 on the cam block operate in the same manner as similar parts in my Patent No. 1,606,290.

The main package hold-down mechanism, best illustrated in Figs. 1 and 2, comprises a substantially Z-shaped foot piece 200 which may be of spring metal, such as spring brass. The forward end thereof is curved upward slightly to avoid hooking into any portion 0f the package with which it might come in contact. This foot piece has an upwardly projecting boss 203 centrally thereof, in which is secured an upwardly extending rod 204.

The rod is adjustably mounted in two vertically aligned bearing portions in a bracket 205. A guide screw 206 (Fig. 2) is threaded into the lower bearing, the guide screw having the inner end thereof formed to ride in a longitudinal slot 201 in the rod to hold it against turning. The upper hearing has a thumb screw 208 mounted to have its inner end engage the rod 209 to secure it in vertically adjusted position in the bracket. The bracket 205 is pivotally mounted on the ends of a pair of parallel links 209 and 2I0, which in turn are pivotally mounted on a bracket 2I3 carried by the frame.

The upper parallel link 209 extends beyond its pivotal mounting on the bracket (Fig. 1), and is pivotally connected at its outer end to an operating link M4. The lower end of the operating link 2I4 (Fig. 2) is pivoted to a lever 2I5, journaled on a rock shaft 2I6, and which in turn is journaled in the frame. A collar 2I1 is secured around the end of the rock shaft 2I6 outwardly from the lever 2I5 to retain the lever against endwise movement on the shaft.

A cam-actuated operating arm 2I8 is keyed to the opposite end of the rock shaft from the lever 2I5, and has its free end projecting forwardly, and provided'with a cam roller 2I9 (see Figs. 2 and the roller being mounted to ride in a cam way 220 in the side of the mutilated gear 55. The normal or at rest position of the mutilated gear is illustrated in Fig. 10. From this it will be noted that the cam track slopes outward almost radially from this starting position of the roller, so that almost immediately upon starting rotation of the mutilated gear in the direction of the arrow, the arm 2I8 will be swung rapidly in a clockwise direction from its position illustrated in Fig. 10 to operate the main package clamping mechanism. That this will occur before either of the pinions I95 or I46 are engaged by the initial toothed portions of their respective zones of the mutilated'gear is illustrated in Figs. 9 and 10. In Fig. 9 the two arcs within which the pinion I46 is successively engaged by the teeth of the mutilated gear are indicated by the bracket marks A and B while in Fig. 10 the two arcs within which the pinion I05 is so engaged are indicated by the bracket marks X and Y.

The operative connection between the camactuated rock shaft 2I6 and the lever 2l5 which is pivoted thereon, is accomplished through a fitting 223 (see Fig.v 2), which is keyed to the rock shaft. A rod 224 is threaded into a boss on the fitting 223, and is secured in position by means of a lock nut 225. An eyed collar 228 is mounted on the rod 224, and has a coil spring 221 hooked therein, the other end of the coil spring being hooked into the opposite end of the lever 2I5 from that to which the lower end of the link 2|4 is pivotally connected. An arm 228 projects axially from the fitting 223 and is positioned to engage a stud 229 which projects laterally from the lever 2| 5 into the path of this arm. The coil spring tends to move the lever 2I5 pivotally in a clockwise direction from its position illustrated in Fig. 1, thereby holding the stud 229 against the arm 228.

Upon a clockwise pivotal movement of the rock shaft 2I6 to the position illustrated in Fig. 1, the lever 2I5 also will be swung clockwise, thereby raising the outer end of the link 2 as illustrated in Fig. 1, and swinging the inner or right hand ends of the parallel links 209 and 2H) and their supported bracket and package clamp downwardly to clamping position.

The maximum pressurewhich the clamp can exert is, of course, limited by the tension of the coil spring 221, since, except for the tension of this spring, the lever 2I5 would be free to pivot counterclockwise. This is an important safety feature, and prevents damage to a package or injury to the operator in case an extra package or the hand of an operator inadvertently should be permitted to come beneath the clamp during its operation.

An additional important safety feature is provided in the break-away fitting on the lower end of the reciprocating rod III. The fitting I35 on the lower end of this reciprocating rod I9 is arranged to release automatically in casethe needle .arm or other parts carried by the cross head I30 should encounter an obstruction during a wrapping operation. Such obstruction might comprise an improperly positioned package, or the hand or arm of an operator. This safety break-away mechanism is illustrated in detail in Figs. 12, 13 and 14.

A block 233 is mounted on the lower end of the rod I9 and is secured thereto by a pin 234. One face of the block is machined out in the form of a recess 235 and a ball bearing roller 236 is mounted to fit within the upper portion of this recess, being secured in position by a cap screw 23] as illustrated in Fig. 14. The head of the cap screw also is employed-to retain a flange plate 24I in position over the roller. The upper end of the flange plate is mounted in a shallow notch in the block 233 provided to receive it, and the lower end of the flange extends downwardly below the roller to hold the fitting on the slide rail I36.

A retaining clip 238 is pivoted on a pin 239 mounted transversely of the lower end of the block 233. The side portions 249 of the lower end of the block 233 (see Fig. 13) are recessed to receive side extensions 243 (see Fig. 14) of the clip member. The central portion of the clip member between these side extensions is shaped to rest against the sloping bottom of the block 233 when the clip is in operating position.

,A bell crank lever 244 is pivoted, as by means of a screw 245 to the side of the block 233, a laterally extending arm 246 of the bell crank lever being positioned in the path of the slide rail I36 when the slide rail is moved upwardly into engagement with the roller 236. A downwardly extending arm 24'! of the bell crank lever is positioned to engage a pin 248 carried by the pivoted clip 238. The pin also is engaged by the hooked lower end of a coil tension spring 249 the upper end of which is hooked into engagement with a pin 250 projecting laterally from the block 233.

In the open or rail-releasing position of the clip 239 illustrated in Fig. 13, the center-line of the tension spring is slightly to the left of the center-line of the pivot 239, and thereby urges the clip to remain in its open or released position. When the slide rail I36 moves upwardly toward the roller 236, the upper face of the slide rail strikes the lower edge of the laterally extending arm 246 of the bell crank lever and thereby urges the bell crank lever to move pivotally in a counterclockwise direction. This forces the lower end of the bell crank lever against the pin 248, thereby urging the clip 238 pivotally in a counterclockwise direction. When the center-line of the tension spring 249 passes to the right of the clip pivot, from the position illustrated in Fig. 13,

the coil spring will urge the clip to continue in this counterclockwise pivotal movement, thereby swinging the clip up into the slide-rail-engaging position of Figs. 12 and 14. No adjustment of the break-away tension is provided in the embodiment illustrated, and ordinarily none is required. However, if desired, the break-away tension can be increased or decreased by substituting for the spring 249 other springs of different tensions, a lighter spring reducing the break-away force required, and a heavier one increasing it.

The package feed mechanism illustrated in Fig. 19 comprises a sliding block 253 slidably mounted between a pair of rails 254 mounted beneath the table top 31, the table top in this instance being provided with a forward extension 255 to provide operating space for the feed mechanism. The sliding block 253 has a pawl 256 pivotally mounted thereon, a pointed end of the pawl being adapted normally to extend upward above the table top as illustrated, and being provided with a rearwardly extending portion 251 which engages the under surface of the slide block, to limit the upward movement of the pawl point. A spring-holding pin 296 is carried by the pawl and projects downward therefrom. The pin 268 has one end of a light coil spring 259 hooked thereto, the other end of the spring =being hooked over the lower end of a pin 266 projecting downwardly from the sliding block.

A bracket 263 projects downwardly from the sliding block, and has pivotal connection at its lower end with the upper end of a link 262. The lower end of this link is pivotally connected to the upper end of a lever 264, the lower end of which is plvotally mounted on a bracket 265 carried by the frame. An adjustable fitting 266 is slidably mounted on the lever 264, the fitting having a transversely mounted pin 261 extending therethrough and riding in an elongated slotted opening 268 in the lever to limit the upward and downward movement of the fitting Onthe lever. A thumb screw 269 is threaded into the fitting and engages the forward face of the lever to secure the fitting in adjusted position. The fitting 266 is pivotally connected as at 216 to the forward end of a link 213, the rear end of which is pivoted to the upper end of a rocking lever 214.

The lower end of the rocking lever 214, is keyed to the rock shaft 2I6 which, as previously described, is rocked first forward and then back, once during each operation of the machine by the lever 2I8 and cam 220 of Fig. 10. Since the arc of movement of the rock shaft, and therefore of the rocking lever 214 are constant, it will be apparent that the throw of the lever 264 may be adjusted by increasing or decreasing the distance of the fitting 266 from the pivotal axis of the lever 264 on which it is mounted. When the rock shaft 2 I6 is swung in a counterclockwise direction, under the action of the cam 220 during the initial phase of the operation of the mechanism, the connected lever 264 likewise will be swung in a counterclockwise direction, thereby moving the lever and its connected slide block to the dot and dash line position of Fig. 19 and bringing the pawl point into position to engage the forward side of the forward package I99.

On completion of the wrapping and knotting operation, when the rock shaft 2 I6 returns toward its solid line position of Fig. 19, the rock shaft will be rotated in a clockwise direction thereby reversing the direction of movement of the parts of the package feeding mechanism, and will swing these parts to their solid line position of Fig. 19. This action moves the pawl 256, and the next package which it engages, to the right, forcing the package against the vertical strip member I63 and tilting it to vertical position. This swings the roller I64 downward, depressing the clutch actuating T-member and thus initiate a new wrapping cycle.

To review briefiy the operation of the mechanism, let us assume that the machine is at rest, motor running, and the forward or left-hand package I99 in Fig. 3 is moved slidably into engagement with the strip member I63 of the temporary hold-down mechanism. The strip member I63 will be swung by this action from its tilted position to its vertical position illustrated in Fig. 19, the stop bar I6I (Figs. 1 and 2) limiting the advance of the package to prevent possible injury to the strip I63 and its associated parts.

This movement of the strip member I63 to vertical position brings the temporary package clamp swings the roller I64, on the lower end of the strip member, downwardly against the head of the T- 'angle member I65 down on top of the package and member I68, depressing the T-member from the dot-and-dash line position of Fig. 19 to the solid line position of that figure.

The left-hand ends of the parallel links 819 and I11 are swung downwardly by this movement of the T-member, moving the composite link I19 downwardly, and thereby swinging the bell crank lever I66 in a counterclockwise direction against the tension of the spring I88 and the weight of the counterweight I90. This withdraws the slip link I95 and permits the spring-urged clutch lever 53 to move to clutch-engaging position.

' Referring now to Figs. 9 and 10, which show opposite sides of the mutilated gear in normal or at rest position, it will be noted, from the relative positions of the pinions I65 and I46, the toothed portions of the mutilated gear which operate them and the position of the cam 22!! and its cam-operated arm 2I8; that the rock shaft operating arm 2I8 is first swung in a clockwise direction from the position illustrated in Fig. 10, thereby moving the main package clamp 200 downwardly into clamping engagement with the package. This movement produced by the rocking of the rockshaft 2I6 simultaneously (see Fig, 19) moves the package feed mechanism forwardly to the dot-and-dash position of Fig. 19, so that the pawl 256 slips under the next package in position to draw it into wrapping position on the next rearward stroke of the package feed mechanism.

Following the bottoming of the main package clamp, the pinion I46 is engaged by the teeth of the mutilated gear, and is rotated through onehalf revolution. This rotates the sprockets i 13 and I44 and their connected crank arms through one-half revolution, raising the cros head I39 upwardly to the position illustrated in Fig. 6. As the cross head leaves its lowermost position, which is the dotted line position of Fig. 5, the lever I66 is raised from engagement with the roller I65, and the weight of this lever, together with the action of the compressed coil spring I66 (see Fig. 15) swings the needle arm in a clockwise direction to the solid line position of Fig. 15.

Returning now to Figs. 9 and 10, it will be noted that the package clamping operation and raising of the cross head I30 above described will occupy approximately 90 of arc of the rotation of the mutilated gear, while in Fig. 10 it will be noted that after approximately 90 rotation of the mutilated gear, the pinion I will be engaged by the teeth on the mutilated gear and will be rotated through one complete revolution. This complete rotation of the pinion I05 (see Fig. 4)

'causes a rotation of the crank 94 due to the one-to-two ratio between the driving and driven sprockets I03 and 95. This half rotation of the crank 94 moves the carriage 69 forward to its maximum limit of movement, but, just before reaching its maximum forward position, which is illustrated in Fig. '7, the pinion I46 again is engaged by the teeth on the mutilated gear, and the cross head is thereby moved downwardly to its lowermost position illustrated in Fig. 7. This brings the ejector bars down in front of the package being wrapped, and ready to move the package rearwardly after the knotting operation has been completed. As the cross head reaches its lowermost position, the lever I54 engages the roller I55 and swings the needle arm sharply in a counterclockwise direction to its dot and dash line position of Fig. 15, thereby swingi the reach of twine carried bythe needle arm into engagement with the twine catcher ll. In this position of Fig. 7 the carriage and cross head dwell while the knotting operation is performed by the knotter beak "I and its associated mechanism, and the twine is severed by the severing knife 282. These knottlng and severing operations are performed on the twine in the manner described in my Patent No. 1,608,290.

Upon completion of the twine knotting and severing operations the pinion I again engages the toothed portion of the mutilated gear and swings the crank 94 through another 180 of arc to the position illustrated in Fig. '4, to return the carriage to its maximum rearward position. During this rearward travel of the carriage the ejector bars push the wrapped package'irom wrapping position and the needle arm lays a new reach of twine beneath the table for the next wrapping operation.

During this same rearward travel of the carrlage the cam roller 2l9 travels upwardly in the cam 220 toward the axis of the mutilated gear as illustrated in Figs. 10 and 19, thereby rocking the rock shaft 2i6 to raise the main package clamp 200 from its clamping position of Fig. 1 to the 'releasing position of Fig. 2.

' in the tilted non-operating position of Fig. 3, and

the machine will remain at rest until a package is inserted to the wrapping position or the clutch operating mechanism is otherwise actuated.

While I have illustrated a preferred embodiment of my invention, many modifications may be made without departing from the spirit of the invention, and I do not wish to be limited to the precise details of construction, but desire to avail myself of all changes within the scope of the appended claims.

I claim:

1. A package wrapping and tying machine comprising a. package supporting table, a twine catcher mounted beneath the table, a carriage reciprocably mounted adjacent to the table, means for reciprocating the carriage longitudinally of the table, a vertically reciprocable twine laying member mounted on the carriage, cyclical operating means normally holding the twine laying member to support an initial reach of twine longitudinally beneath a package supporting area of the table, the forward end of said reach being held by the twine catcher, said cyclical operating means being operable to move the twine laying member in an orbit first upwardly, then forwardly at package-clearing height, and then downwardly at package-clearing distance, to complete a wrap of twine around a package supported on the table, tying means mounted adjacent the terminal end of the wrapping cycle and adapted to grip the ends of the twine wrap thus formed and secure them together, and severing means mounted to sever the twine on the completion of the tying operation, said cyclical operating means being coordinated in operation with the tying and the severing means to operate, after the severing means has completed severing the twine, for moving the carriage rearwardly to lay an initial reach of twine for the next package wrap.

2. A package wrapping and tying machine comprising a package supportingtable, a twine catcher mounted beneath the table, a carriage mounted adjacent the table, means for reciprocating the carriage longitudinally of the table, a vertically reciprocable member mounted on the carriage and having a portion thereof projecting over the table, a twine laying member extending downwardly therefrom and having an oriflce'Tn the lower end thereof, cyclical operating means normally holding the twine laying member in its maximum downward and rearward position to clear a package wrapping area of the table ahead of the twine laying member and to support a reach of twine having its forward end seized by the twine catcher beneath a package supporting area of the table, said cyclical operating means being operable to move the twine laying member in an orbit around the other three sides of a package supported on the package wrapping area of the table to complete a wrap of twine around such package, securing means mounted adjacent the terminal end of the wrapping cycle and adapted to grip the ends of the twine wrap thus formed and secure them together, and severing means mounted to sever the twine on the completion of the tying operation, the. cyclical operating means being coordinated in operation with the tying and the severing means to operate, after the severing means has completed severing the twine, for moving the carriage rearwardly to lay the initial reach of twine for the next package wrap, and to clear the package wrapping area 01' the table ahead of the twine laying member.

3. A package wrapping and tying machine comprising a package supporting table, a twine catcher mounted beneath the table, a carriage mounted adjacent the table, means for reciprocating the carriage longitudinally of the table, a vertically reciprocable member mounted on the carriage, a transversely extending cross-head carried by the vertically reciprocable member and extending laterally over a package wrapping area of the table, a twine laying member mounted on the cross-head to depend therefrom and having a normal downward and rearward position to support a reach of twine, having its forward end seized by the twine catcher, longitudinally beneath the package wrapping area of the table, a package ejector mounted on the cross-head, cyclical operating means operatively connected to' the can-iage and to the cross-head to move the cross-head vertically and the carriage longitudinally in alternating reciprocal motions to carry the twine laying arm through a substantially rectangular orbit. thereby laying a wrap of twine around the package supporting area of the table to bring the package ejector in front of the package wrapping area of the table, securing means mounted adjacent the terminal end of the wrap, said securing means being positioned to secure the ends of the wrap, severing means mounted to sever the twine on completion of the securing operation, said cyclical operating means thereafter moving the cross-head and the package ejector mounted thereon rearwardly, thereby to sweep the package wrapping area rearwardly to eject a package from said wrapping area.

4. A package wrapping and tying machine comprising a package supporting table, a. twine catcher mounted beneath the table, a vertically and horizontally reciprocable member mounted to overlie the table, a twine laying member mounted on the reciprocable member to depend therefrom, a package ejector mounted on the reciprocable member, cyclical operating means operatively connected to the reciprocable member normally to hold it rearwardly beyond a package wrapping area of the table, and to move the reciprocable member in alternate vertical and horizontal reciprocal motion to carry the twine laying member through a substantially rectangular orbit. thereby laying a wrap of twine around a package positioned initially ahead of the reciprocable member and subsequently moving the reciprocable memher to a position ahead of the package, twine securing means mounted to secure the ends of the wrap upon its completion, severing means mounted to sever the twine on completion of the securing operation. said cyclical operating means thereafter moving the reciprocable member and the package ejector mounted thereon rearwardly. thereby to eject the wrapped package rearwardly from the wrapping area of the table.

5. A package wrapping and tying machine comprising a package supporting table, a twine catcher mounted beneath the table. a twine laying member mounted above the table to extend downwardly toward the table. a package ejector mounted rearwardly of the twine laying member. cyclical operating means operatively connected to the twine laying member to move the twine laying member through a substantially rectan ular orbit to lay a wra of twine around a package of predetermined size positioned on the table ahead of the initial position of the twine laying member, thereby moving the package ejector ahead of the package, twine securing means mounted to secure together the ends of the wrap, severing means mounted to sever the twine on completion of the securing operation. said cyclical o erating means thereafter moving the twine laying member and the package ejector mounted thereon rearwardly thereby to eject the wrapped package rearwardly from the wrapping area of the table.

6. In combination in a package wrapping and tying machine including a packa e supportin table and a twine catcher mounted beneath the table, a carria e mounted for longitudinal reciprocation adjacent the table. a vertically reciprocable member mountedon the carriage, a twine laying member pivoted on the vertically reciprocable member and extending downwardly therefrom, said twine laying member having a twine laying orifice adjacent its lower end, means normally holding the vertically reciprocable member and the carriage in their rearward, downward positions, thereby to support a reach of twine beneath a package wrapping area of the table, the forward end of said reach being adapted to be gripped by the twine catcher. cyclical operating means associated with the carriage and the vertically reciprocable member to move the orificed lower-end of the twine laying member first upwardly to clear a package of predetermined height and length supported in wrapping position on the table, then forwardly to clear such package. and then downwardly to lay a wrap of twine about such package and to bring the orificed lower end of the twine laying member, below and ahead of the twine catcher. and means operatively engaging the pivoted twine laying arm as it approaches its lowermost forward position, pivotally to move the twine laying member to swing the lower end of the twine laying member rearwardly to force the reach of twine extending from 7 said twine laying orifice into gripped engagement with the twine catcher,

7. In combination in a package wrapping and tying machine including a package supporting table and a twine catcher mounted beneath the table. a vertically and horizontally reciprocable member mounted over the table, a twine laying member pivoted on the vertically and horizontally reciprocable member and extending downwardly therefrom, said twine laying member having a twine laying orifice adjacent its lower end, cyclical operating means normally holding the vertically and horizontally reciprocable member in its rearward, downward position, thereby to support a reach of twine extending from the twine catcher to the orifice in the lower end of the twine laying member, said cyclical operating means being operable to move the twine laying lower end of the twine laying member first upwardly to clear a package'of predetermined height supported on the table, then forwardly beyond the package, and then downwardly to bring the twine laying lower end of the twine laying member below and ahead of the twine catcher, and stop means engaging a portion of the pivoted twine laying member as it approaches its lowermost forward position, pivotally to move the twine laying member to swing the reach of twine extending from the orificed lower end thereof rearward into engagement with the twine catcher.

8. In combination in a package wrapping and tying machine including a package supporting table and a twine catcher mounted beneath the table, a vertically and horizontally reciprocable member mounted over the table, a twine laying member pivoted on the vertically and horizontally reciprocable member and extending downwardly therefrom, said twine laying member having a twine laying orifice adjacent its lower end, spring means normally urging forwardly the lower end of the twine laying member, a cam lever secured to the twine laying member and projecting laterally therefrom, cyclical operating means normally holding the vertically and horizontally reciprocable member in its rearward, downward position, thereby to support a reach of twine extending from the twine catcher to the twine laying orifice in the lower end of the twine laying member, said cyclical operating means being operable to move the twine laying lower end of the twine laying member first upwardly to clear a package of predetermined height supported on the table, then forwardly beyond the package, and then downwardly to bring the twine laying lower end of the twine laying member below and ahead. of the twine catcher, and stop means engagin the laterally projecting lever on the pivoted'twine laying member as it approaches its lowermost forward position, pivotally to move the twine laying member to swing the reach of twine extendingfrom the orificed lower end thereof rearward into engagement with the twine catcher,

9. In combination in a package wrapping and tying machine including a frame and a package 1 extending portion having a twine laying orificein the lower end thereof. a carriage operating lever pivoted at one end thereof on the frame, means connecting the other end of the lever to the carriage, cyclical operating means mounted on the frame and operatively connected to the lever and to the vertically reciprocable twine laying member, alternately to move the lever andthe vertically reciprocable member to move the oriflced lower end of the twine laying member through a substantially rectangular orbit over and around a package supporting area of the table, the connection of the cyclical operating means to the lever comprising a crank rotatably.

connected to the cyclical operating means, and a rod connected from the crank to the lever, the crank throw and connecting rod length being adjustable to vary the throw of the crank and simultaneously to change the length of the connecting rod proportionately thereto whereby the forward position of the carriage during a reciprocating movement is maintained constant throughout the range of adjustment of the crank throw.

10. A package wrapping and tying machine comprising a frame, a package supporting table mounted on said frame, a carriage mounted for horizontal reciprocation adjacent to the table, a vertically reciprocable twine laying member mounted on the carriage above the table and having a portion thereof extending downwardly toward the table, said downwardly extending portion having a twine laying orifice in the lower end thereof, a carriage operating lever pivoted at one end thereof on the frame, means connecting the other end of the lever to the carriage,

cyclical operating means mounted on the frame and operatively connected to the lever and to the vertically reciprocable twine laying member, alternately to move the lever and the vertically reciprocable member to move the twine laying-- anchoringof the rod by said anchor member to vary the throw of the crank and simultaneously to change the link length proportionately to the change in the throw, thereby to maintain constant the maximum forward position of the car'- riage during a reciprocating movement throughout the entire range of adjustment of the crank throw.

ll. A package wrapping and tying mechanism comprising a frame, a package supporting table mounted on the frame, a horizontally reciprocable member mounted adjacent the table to reciprocate lengthwise thereof, a vertically reciprocable .cross-head mounted on the horizontally reciprocable member to reciprocate therewith, a twine laying member extending downwardly from the cross-head toward the table and having an apertured lower end thereof normally positioned beneath the table to support a reach of twine beneath a package supporting area of the table, a lever pivotally mounted on the frame, means operably connecting the lever to the horizontally reciprocable member, a'crank rotatably mounted on the frame, cyclical operating means operativeiy connected to the crank for intermit tently rotating the crank, a connecting rod adjustably connecting the crank to the lever to rock the lever back and forth on rotatable movements of the crank, releasable locking means acting bethe connecting rod to the crank during an adjustment of the crank throw and connecting rod length, adjusting means interconnecting said crank, connecting rod, and lever for effecting slmultaneous changes in the crank throw and in the effective length of the connecting rod, said adjusting means being constructed and arranged to provide a fixed ratio of two to one between the change in the crank throw and the change in the effective length of the connecting rod to maintain constant the forward position of the lever and its connected horizontally reciprocable member throughout the entire range of adjustment of the crank throw.

12. A package wrapping and tying mechanism comprising a frame, a package supporting table mounted on the frame, a horizontally reciprocable member mounted adjacent the table to reciprocate lengthwise thereof, a vertically reciprocable cross-head mounted for vertical reciprocation onthe horizontally reciprocable member, a twine laying member extending downwardly from the cross-head toward the table and having a twine laying lowerend thereof normally positioned beneath the table to support a reach of' twine beneath a package supporting area of the table, a lever pivotally mounted on the frame, means connecting the lever to the horizontally reciprocable member, a crank rotatably mounted on the frame, cyclical operatingmeans operatively connected to the crank for intermittently operating the crank, a connecting rod connecting the crank to the lever to rock the lever'back and forth on a rotative movement of the crank, a pin adjustably mounted on the crankand adapted to be secured in adjusted position thereon, a post pivoted on the lever, a rod connecting the pin on the crank to the post on-the lever, said rod having single thread screw connection with the crank pin and double thread screw connection with the post on the lever, an anchor normally permitting free relative movement between the rod and the crank, said anchor being movable into anchoring engagement between the crank and the rod, releasable means holding the rod against turning whereby, upon release of the pin for adjustment, release of the rod for turning and anchoring of the rod against endwise movement to the crank, the length of the connecting rod between the crank and the lever and the length of the crank throw are adapted to be changed by rotation of the connecting rod, the changes in the effective length of the connecting rod and in the length of the crank throw being in the ratio of one to two, to maintain constant the forward position of the lever and its connected horizontally reciprocable tween the connecting rod and the crank to lock Ii member throughout the entire range of adjustment of the crank throw.

13. A package wrapping and tying mechanism comprising a frame, a package supporting table mounted on the frame, a horizontally and vertically reciprocable member mounted above the table, a twin laying member carried by the reciprocable member and extending downwardly toward the table, said twine laying member having an oriilced lower end normally positioned beneath the table to support a reach of twine beneath a package supporting area of the table, cyclical operating means operatively connected to the reciprocable member alternately to reciprocate said member in a vertical and a horizontal direction to move the oriflced lower end of the twine laying member in a substantially rectangular orbit around a package supporting area of the table,

and a lever and connected stroke-adjusting means connecting the cyclical operating means to the reciprocable member, the adjusting means being so arranged that for a given change in the length of the horizontal reciprocation of the reciprocable member there is effected a displacement of the rearmost position of the reciprocable member double such change in length to maintain constant the forward position of the lever and its connected horizontally reciprocable member throughout the entire range of adjustment of horizontal reciprocation of the reciprocable member.

14. A package wrapping and tying mechanism comprising a frame, a package supporting table mounted on the frame, a horizontally reciprocable member mounted beneath the table, a vertically reciprocable cross-head mounted for vertical reciprocation on the horizontally reciprocable member, a twine laying member extending downward- 1y from the cross-head'and having an orifice in the lower end thereof normally positioned beneath the table to support a reach of twine lengthwise beneath a package supporting area of the table, cyclical operating means mounted on the frame, means connecting the cyclical operating means to the horizontally reciprocable member to move last said member reciprocally forward and back at predetermined points of the cycle of operation, a pair of inter-connected cranks, a rail mounted on the outer ends of the cranks to be swung alternately upwardly and downwardly on a rotation of the cranks, a fitting carried by the cross-head and having slidably releasable connection with the rail to reciprocate the cross-head vertically on a rotation of the cranks and their supported rail, operative connection between the cyclical operating means and the cranks to move the cranks and thereby the cross-head in vertically reciprocating movements at predetermined points in the cycle of said cyclical operating mechanism, the vertically reciprocating movements being alternated with the horizontal reciprocating movements of the horizontall reciprocable member to move the orificed lower end of the twine laying member in a substantially rectangular orbit about a package wrapping space on the table.

15. A package wrapping and tying mechanism comprising a frame, a package supporting table mounted on the frame, a horizontally reciprocable member mounted beneath the table, a vertically reciprocable cross-head mounted for vertical reciprocation on the horizontally reciprocable member, a twine laying member extending downwardly from the cross-head and having an orifice in the lower end thereof normally positioned beneath the table to support a reach of twine lengthwise beneath a package supporting area of the table, cyclical operating means mounted on the frame, means connecting the cyclical operating means to the horizontally reciprocable member to move last said member reciprocally forward and back at predetermined points of the cycle of operation, a pair of inter-connected cranks, a rail mounted on the outer ends of the cranks to be swung alternately upwardly and downwardly on a rotation of the cranks, a fitting carried by the cross-head and having slidably releasable connection with the rail to reciprocate the cross-headvertically on a rotation of the cranks and their supported rail, operative connection between the cyclical operating means and the cranks to move the cranks and thereby the cross-head in vertically reciprocating movements at predetermined points in the cycle of said cyclical operating mechanism,

the vertically reciprocating movements being alternated with the horizontal reciprocating movements of the horizontally reciprocable memher to move the orificed lower end of the twine laying member in a substantially rectangular orbit about a package wrapping space on the table, the connection between the vertically reciprocable member and the rail comprising a block, mounted on the vertically reciprocable member, and having a recess therein adapted to receive the rail, a roller mounted in the recess and adapted to ride on the rail, and a spring held clip mounted to em gage the opposite side of the rail from the roller, the clip being releasable from the rail by a force in excess of the spring-holding force of the clip to free the rail from operative connection with the vertically reciprocable member.

16. A package wrapping and tying mechanism comprising a frame, a package supporting table mounted on the frame, a horizontally reciprocable member mounted beneath the table, a vertically reciprocable cross-head mounted for vertical reciprocation on the horizontally reciprocable member, a twine laying member extending downward from the cross-head and having an orifice in the lower end thereof normally positioned beneath the table to support a reach of twine lengthwise beneath a package supporting area of the table, cyclical operating means mounted on the frame, means connecting the cyclical operating means to the horizontally reciprocable member to move last said member reciprocally forward and back at predetermined points of the cycle of operation, a pair of interconnected cranks, a rail mounted on the outer ends of the cranks to be swung alternately upwardly and downwardly on a rotation of the crank, afittingcarried by the cross-head and having slidable releasable connection with the rail to reciprocate the cross-head vertically on a rotation of the cranks and their supported rail, operative connection between the cyclical operating means and the cranks to move the cranks and thereby the cross-head in vertically reciprocating movements at predetermined points in the cycle of said cyclical operating mechanism, the vertically reciprocating movements being alternated with the horizontal reciprocating movements of the horizontally reciprocable member to move the orificed end of the twine laying member in a substantially rectangular orbit about the space occupied by a package on the package supporting table, the connection between the vertically reciprocable member and the rail comprising a block mounted on the vertically reciprocable member and having a. rail-receiving recess therein, a roller mounted in the recess and adapted to ride on the rail, a clip pivoted to a side of the block below the recess to engage the opposite side of the rail from the roller, a coil spring mounted to urge the clip to closed, rail-holding position when the clip is in rail-engaging position, said spring being positioned to swing, on a release of the clip, past dead center of the pivot, thereby to hold the clip in open, rail-releasing position, and a lever, having a first portion thereof in the path of the rail entering the recess, a second portion of the lever being positioned against a clip element, automatically to swing the clip to rail-engaging position when the rail enters the recess to strike the first lever portion.

17. A package wrapping and tying mechanism comprising a frame, a package supporting table mounted on the frame, a vertically and horizontally reciprocable member mounted over the ta-

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