US2299062A

US2299062A - Punching machine

Info

Publication number: US2299062A
Application number: US394451A
Authority: US
Inventors: Theodore T Youngfelt
Original assignee: United States Gypsum Co
Current assignee: United States Gypsum Co
Priority date: 1941-05-21
Filing date: 1941-05-21
Publication date: 1942-10-13
Anticipated expiration: 1959-10-13

Description

Oct. 13, 1942. T. 'r. YOUNGFELT PUNCHING MACHINE Filed May 21, 1941 7 Sheets-Sheet 1 o I N INVENTOR fimzf" l-W v- I ATTORN EY5.

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PUNGHING MACHINE Filed May 21, 1941 '7 Sheets-Sheet 4 INVENTOR 'ATTORNE .5.

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'7 Sheets-Sheet 5 Filed May 21, 1941 ATTORNEYS.

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PUNCHING MACHINE Filed May 21, 1941 7 Sheets-Sheet 6 Center line INVENQR We 1: o m J0 WHI 1:7 ATTORNEYS 1942- 'r. T. YOUNGFELT PUNCHING MACHINE 7 Sheets-Sheet 7 Filed May 21, 1941 Patented Oct. 13, 1942 PUNCHING mcnnmi Theodore T. Youngfelt, Hinsdale, 111., assignor to United States Gypsum Oommby, Chicago, Ill., a corporation of Illinois Application May 21, 1941, Serial No. 394,451

21 Claims.

This invention relates to punching or perforating machines, and more particularly to machines for punching or perforating moving webs or strips of gypsum plasterboard and the like as the webs are discharged from a suitable web-forming apparatus. The invention is an improvement over punching machines such; for instance, as are disclosed and claimed in the copending application of Otto P.-Haegele, for Plasterboard manufacturing machine, now Patent No. 2,272,703, issued February 10, 1942.

The present invention is particularly directed to an improvement in the punching .portion of the mechanism illustrated in the above-identified copending application, and'may, of course, be used independently of any cutting and scoring mechanism such as is therein disclosed and claimed. However, it is suitable for use therewith, and the transmission and driving means for the cutting mechanism may be substantially as disclosed in the Haegele application.

The moving web or webs, as received from the web-forming apparatus, are preferably punched or perforated and cut into predetermined lengths while the web is still in a moist condition, that is, before it is delivered to the usual drier. The apertures or perforations may be of any suitable size, but are preferably comparatively large and symmetrically spaced throughout the extent of the boards to be cut from the web, and severing and scoring operations similar to those described in the Haegele application may be performed at predetermined intermediate points between transverse rows of perforations.

It is an object of the present invention to provide an improved mechanism whereby the punching operations are performed during the continu-.

ous movement of the web and in which the movement of the perforators or punches through the web, and in fact throughout their entire cycle, is so related to the movement of the web a relationship of the various portions of this cycle v to the web movement, together with the particular mechanism for producing the punch cycle, provides a machine whereby the successive operations may be performed at high speed in a manner to provide smooth wall perforations and without tearing or otherwise mutilating the usual paper covering of the plasterboard web.

In the manufacture of perforated gypsum board,'considerable difficulty has been experienced in the past in securing a satisfactory punching machine which would operate successfully at high speeds. It is, therefore, an object to provide a perforating machine which will operate satisfactorily when the web is moving at comparatively very high speeds, such, for instance, as from to or more feet per minute.

Although certain plasterboard punching machines heretofore known in the art have been largely satisfactory for the uses intended, certain parts of the punch mechanism have often been wrecked by foreign material such as pieces of metal and the like accidentally included in the plasterboard core. Difficulties have also been encounteredjbecause of noise and excessive vibration. Furthermore, in some cases the punches travelled at a comparatively low speed through the board so that the punched holes were not as clean cut as may sometimes be desired.

it is, therefore, an object of the present invention to provide a perforating machine in which balanced parts for operating the punches are so arranged that the machine may be operated at extremely high speeds.

Furthermore, it is an object to provide a perforating machine in which the movement of the punches into and through the web and the withdrawal thereof is at a high rate of speed, thereby insuring clean cut punched holes.

A further object is to provide a punch mechanism construction including suitable safety devices, so that the punch or the mechanism will not be wrecked when foreign material accidentally comes between the punch and the die.-

Further objects will be apparent from the specification and the appended claims.

In the drawings:

Fig. 1 is a top plan view of one embodiment of the invention including web perforating and web severing and v scoring devices.

Fig. 2 is a side elevation of the web punching mechanism partly in section on a line substantially corresponding to line 22 of Fig. 1.

Fig. 3 is an enlarged top plan view of the pera line substantially corresponding to line 5-5 of Fig. 2 and further illustrates the punch and die and operating mechanism therefor.

Fig. 6 is a fragmentary detail view partially in section of the punch connecting rod elements and shear pin connection;

Figs. 7, 8, 9, 10, and 11 are diagrammatic sectional elevations illustrating different positions of the punch and operating mechanism therefor during a single perforating cycle.

Fig. 12 is a diagram illustrating the punch operating cycle relative to th plasterboard and to a single revolution of the crankshaft.

Fig. 13 is a diagrammatic view illustrating the relationship of the punching cycle to the vertical and horizontal reciprocating movements of the punch and die.

Referring to the drawings in detail, the embodiment illustrated comprises suitable side frames i and 2 which are spaced sufficiently to allow a plurality of plasterboard webs to pass therebetween. These side frames are connected together by means of suitable cross bars preferably in the form of channels or I-beams 3. and I such as illustrated particularly in Fig. 2.

A conveyor (not shown) of any suitable type, preferably a belt supported on rollers, is provided to continuously deliver an imperforate web or a plurality of webs 5 (Fig. 1) from a remotely positioned web-forming mechanism to the perforating and cutting mechanisms from which the cut lengths may be removed by means of a suitable discharge conveyor. The web first passes through the perforating or punching mechanism and then between two rotating cutter units positioned above and below the web, respectively, the cutters of which are operable either to score the web or to cut the web into predetermined lengths as it passes therebetween.

The cutting and scoring mechanism in the present embodiment is illustrated at 6 (Fig. 1) and may be of the same general type as illustrated and described in the above-identified copending application and may be operated by any suitable mechanism by which the cutting operation is synchronized with the perforating mechanism so that the webs are preferably severed or scored at predetermined points between transverse rows of perforations.

In the present instance, the cutting mecha-- nism comprises a transmission 1 associated with the main driving mechanism of the perforator so that a suitablesynchronous operation is obtained. It is believed unnecessary to describe this mechanism in detail. The perforating mechanism of the present invention is driven from a shaft 8 by means of a suitable transmission including bevel gears 9, one of which latter is secured to a transverse crankshaft ll supported in suitable bearings in the frame of the machine, as shown particularly in Fig. 2. A suitable brake and control mechanism, such for instance as shown in the previously mentioned copending application, may be used in connection with the present invention, and it is therefore thought unnecessary to illustrate and describe that mechanism in connection with the present application.

The crankshaft I0 is the driveshaft of the entire actual perforating mechanism. The perforating or punching mechanism includes a punch and die carriage comprising a frame ll mounted for horizontal reciprocating movement simultaneously with the vertical reciprocating movement of the punches. The punch and die carriage comprises a lower cross bar [2 positioned below the web-and adapted to support a row of dies, and a very similar upper cross bar I! positioned above the web for guiding the punches in their vertical movement through the web and into the dies. The bars I! and iii are secured together at each end by means of a guide block or bearing block I4 secured thereto as shown in Fig. 2. The blocks is are supported for horizontal reciprocation on horizontal fixed guide shafts I5, one of which latter is mounted at each side of the machine so that the punch and die carriage may horizontally be reciprocated thereon. The horizontal reciprocation of the carriage is accomplished by means of cams I on the crankshaft [0 previously referred to (Fig. 2).

The cams l6 co-operate with a pair of diametrically opposed follower rollers H, the latter being mounted on bell crank cam levers l0 pivoted at '9 on the frame (Fig. 4). The levers I! are provided with downwardly extending arms 20, which latter are forked at the respective lower end thereof and provided with suitable rollers engaging in slots 2| in collars 22 on the opposite ends of the carriage il. One of these collars 22 is preferably provided on each of the bearing blocks II to co-operate with its respective cam arm, whereby, during part of each rotation of the crankshaft III, the punch and die carriage II will be moved in the direction of movement of the web and the intermediate part of this movement will be at the same speed as the speed of the web, during which intermediate period-the punches will operate to perforate the web and withdraw therefrom. The carriage and punches will complete their cycles after the punches are raised sufllciently to clear the web. In Fig. 4 one of the bell cranks l8 and its associated parts is shown in full lines in its central position, and its respective extreme positions in either direction are indicated by dotted lines.

A transverse row of punches is supported on the upper bar I! of the carriage II for lateral movement therewith and for vertical movement relative thereto. Each punch comprises a cylindrical punch member 23 (Fig. 5) secured to a piston 24, the piston and punch thereon being arranged to reciprocate vertically in an open end cylinder 25. A row of dies 26 is supported in the lower bar I! of the carriage II and each die is in vertical alignment with its associated punch. Each of the punch cylinders 25 may be supplied with lubricant through a flexible conduit 21 leading from a suitable oil cup 22 mounted on the frame.

Each punch piston 24 is provided with a connecting rod 24a pivotally attached thereto and connected to an arm 29, the latter being secured to an oscillatable shaft Ill. The shaft 20 is positioned below and at one side of the crankshaft III and is mounted to oscillate in suitable bearings in the frame of the machine. The oscillatable shaft 30 is also provided with a downwardly extending arm 3! secured thereto and connected by means of a link 32 to a crank pin 33 forming a part of the crankshaft III. The oscillating shaft 30 and

arms

29 and 3| secured thereto form the equivalent of a bell crank having-a plurality of punch-operating or work arms and a single shaft-oscillating or power arm.

The embodiment illustrated is designed to simultaneously punch a traverse row of four holes in each of three moving plasterboard webs. Therefore, twelve punches and dies are used, as shown in detail in Fig. 2, the twelve punches being driven by two oscillating shafts 2| each of which is operated from the crankshaft III by means of a single link 32. It will be obvious that any number of punches may be operated from a crankshaft by an equivalent arrangement.

The above described mechanism provides a compound lever and link arrangement whereby the actual perforating and the withdrawal of the punch from the gypsum board is performed during a small portion of the revolution of the crankshaft and at a time when the punch and the connecting rod 24a are in substantially vertical alignment and closely adjacent the vertical axial plane of the crankshaft Ill. The structure and relationships shown also enables a suitable balancing of the crankshaft II! by means .of weighted portions 34, which compensates for the moving parts driven by the crankshaft. The relationship 24a. This is illustrated in detail in Fig. 6 and comprises a tubular portion 35 pivotally connected to the piston 24, and a rod 36, which latter is telescoped in the tubular portion 35 with its opposite end 31 pivotally connected to the operating arm 29. of the bell crank. The tubular member 35 is secured to the rod 36 by means of a shear pin 38. This pin is of only sufiicient strength to operate the punch under normal conditions and will shear if the punch meets with any abnormal resistance. The tubular member or sleeve 35 is provided with diametrically opposed slots 39 adapted to receive the ends of a pin 40 inserted in a suitable opening in the rod 36. This provides a lost motion connection for the punch whenever the pin 33 is sheared and retains the parts in assembled relation although rendering the punch inoperative to perforate the plasterboard.

In the present embodiment the machine is designed so that the horizontal movement of the punch and die is two inches. That is, during a complete cycle, the punch and die travel two inches in the direction of forward movement of the web and then return to the starting point for a succeeding cycle. During an intermediate portion of the forward movement of the punch and die, they travel horizontally at the same speed as the web, and the actual perforation of the web and withdrawal of the punch therefrom occurs during this intermediate period. The actual perforating and withdrawal of the punch from the web takes place during a comparatively small portion of the revolution of the crankshaft Ill. The intermediate portion of the forward movement of the punch and die in which they are travelling at the same speed as the web is, in the present machine, substantially 1%;

inches. The perforating of the web and the withdrawal of the punch takes place during this period but does not necessarily require the full length of this intermediate movement. In fact, in the present embodiment, the punch is only in contact with the web during of an inch of horizontal movement. All of the remainder of the cycle is, therefore, used for returning the punch to the next actual web contacting position.

The movement of the punch and the relationship of the various elements during a cycle is illustrated in Figs. 7 to 11, inclusive, and is diegrammatically shown in Figs. 12 and 13.

The crank shaft II will be considered as rotating in a clockwise direction, as viewed in Figs. '7 to 11. During such rotation of the crank the link 32 connecting the crank 33 to the power arm of the bell crank, which bell crank comprises the fulcrum 30, the work arm 33, and the power arm 3|, partakes of a compound movement having three components; 1. e., pivotal movement about the crank 33, pivotal movement about the connection to the arm 3|, and bodily longitudinal movement. It is of course only the first and the third of these components that are effective to cause movement of the work arm 29 and the connecting rod 24a, since pivotal movement of the link 32 about its lower pivot may occur independently of a'nymovement of the bell crank structure about its fulcrum. Y

In Fig. 7 the punch 23 and the operating mechanism are shown in positions wherein the punch is a substantial distance above the board 5, and it will be observed that in this portion of the cycle the movement of the crank 33 is such as to provide a large component of swinging movement of the link 32 about its lower pivot, the path of movement of the crank 33 during this portion approaching tangential relation to the are prescribed by the upper end of the arm 3| when the arm swings about its lower pivot. Accordingly, only a limited longitudinal movement and a limited pivotal movement of the link 32 about the crank 33 occurs.

In Fig. 8 the parts are shown in positions wherein the crank 33 has moved through a sub-' stantial angle from the position of Fig. 7, but it will be observed that the punch 23 and the bell crank structure have moved through only a small distance due to the fact that most of the crank movement in this portion of the cycle is taken up, as indicated above, by swinging movement of the link 32 aboutits lower pivot. In Fig. 8 the crank has just entered the portion of the cycle wherein only a limited swinging movement of the link 32 about its lower pivot is possible, since such movement would require the upper end of the link to move substantially at right angles to this portion of the path of the crank. As the crank 33 moves to the position of Fig. 9, substantially all of the crank movement is converted into bodily movement of the link 32 and accordingly the punch moves at an accelerated rate from the position of Fig. 8 to the position of Fig. 9, wherein the punch is shown at its point cf contact with the board or web 5.

The punch continues to move at substantially this accelerated fate from the position of Fig. 9 until the crank 33 reaches a point slightly beyond the position shown, and the punch then quickly slows down so as to come to rest momentarily at the lowermost position shown in Fig. 10. Only 27 of crank movement occurs between the positions of Figs. 9 and 10, and it is during approximately the first 7 of such movement that the punch, travelling at its accelerated rate,

proximately 33 causes a quick retraction of the punch, since during a substantial and latter portion of this 33 range the path of the crank 33 is so related to the lower pivot of the link 32 as to prevent swinging movement of the link about its lower pivot. Accordingly, the link moves bodily, quickly to accelerate the punch.

-It will thus be seen that the operating mechanism for the various punches is effective to cause a quick thrust and retraction of the punches during the portion of the punch stroke wherein the punch is passing through and back out of the board or web 5, and this quick thrust and retraction is produced by a constant speed rotation of the crank shaft ll.

Fig. 12 is a diagram illustrating the relative movement of the punch during actual perforat-- ing contact with the gypsum board as compared to the movement of the punch throughout the remainder of the cycle. From this chart it will be apparent that during actual perforation the punch is in contact with the gypsum board through only approximately 61 of rotation of the driveshaft. No attempt has been made in this diagram to illustrate accurately any horizontal movement, but is only intended to illustrate the various portions of the vertical cycle with respect to a 360 rotation of the driveshaft.

Fig. 13 is a diagrammatic view illustrating, by the curve I, the path of the face of the punch at the axial line thereof and, by correspondingly numbered straight lines, the position of the various elements of the transmission at certain points in the cycle. The transmission, including the bell crank, is illustrated by heavy full lines when the punch is at the highest point in its path or cycle; with light full lines when the punch is at the bottom of its stroke; and with dotted lines when the punch is at the start and at the end of the actual perforating and withdrawal movement. In order further to clarify the diagrammatic illustration of Fig. 13, the work arm ll of the bell crank is indicated by double lines so that its various positions may readily be distinguished from the positions of the power arm 29. As heretofore noted, the actual perforation requires only a 27 movement of the crankshaft, and this is during the most efficient part of the crankshaft cycle. The actual withdrawal of the punch from the board is accomplished during only 33 movement, and the remaining 299 is used for the completion of the cycle, during which time the punch is free from the board.

It is intended, of course, that the invention should not be limited to the specific embodiment or embodiments disclosed herein, since modifications may be made, and it is contemplated, therefore, by the appended claims to cover any such modifications as fall within the true spirit and scope of this invention.

Having thus described this invention, what is claimed and desired to be secured by Letters Patent is:

1. In a perforating machine for a continuously moving gypsum web, the combination with a horizontally reciprocating punch and a power operated crank in vertical transverse axial alignment with said punch, of a bell crank and link transmission between said crank and said punch, said transmission being constructed to cause said punch to perform the actual perforating operation and withdrawal from said web during a comparatively short intermediate portion of the forward horizontal movement of said punch.

2. In a perforating machine for a continuously moving gypsum web, the combination with a power operated crankshaft. a punch, and means for reciprocating said punch through a compara-- tively short horizontal cycle, of means for vertically reciprocating said punch through a materially longer vertical cycle than its horizontal cycle, said last means comprising a bell crank and link connection between said crank and said punch, the pivotal relationship of said connection being arranged so that the actual perforating and withdrawal operation occurs during a comparatively short intermediate portion of the forward horizontal stroke and at substantially the highest vertical speed of said punch.

3. A punch operating mechanism for a vertically and laterally reciprocating gypsum board punch comprising a power shaft substantially in the transverse vertical axial plane of the path of said punch, a bell crank having its fulcrum below said shaft and at one side of said plane and with its work pivot and power pivot operable in a path closely approaching a tangent to said plane, a connecting rod between said work pivot and said punch, a link connecting said power pivot to a crank on said power shaft, said connections being so related that when the punch is at the lower end of its vertical stroke said work pivot is closely adjacent said vertical plane and said power pivot is at its lower outermost position remote from said plane.

4. A punch operating mechanism for a vertically and laterally reciprocating gypsum board punch comprising a power shaft substantially in the transverse vertical axial plane of the path of said punch, a bell crank having its fulcrum below said shaft and at one side of said plane and with its work pivot and power pivot operable in substantially coincident paths closely approaching a tangent to said plane, a connecting rod between said work pivot and said punch, a link connecting said power pivot to a crank on said power shaft, said connections being so related that when the punch is at the lower end of its vertical stroke said work pivot is closely adjacent said vertical plane and said power pivot it at its lower outermost position below said fulcrum and remote from said plane.

5. A punch operating mechanism for a vertically and laterally reciprocating gypsum board punch comprising a power shaft substantially in the transverse vertical axial plane of the path of said punch, a bell crank having its fulcrum below saidshaft and at one side of said plane and with its work pivot and power pivot operable in an arc closely approaching a tangent to said plane, a link connecting said work pivot with said' punch, and a link connecting said power pivot to a. crank on said power shaft, said connections being related so that when the punch is adjacent the lower end of its vertical stroke said work pivot is closely adjacent said vertical plane.

6. In a perforating machine for a continuously moving plasterboard web, a punch and co-operating die in perforating relationship to said web, means to reciprocate said punch and die parallel with said web movement, means to perpendicularly reciprocate said punch relative to said web, said last means comprising an oscillatable arm pivoted at one side of the axial plane of said punch, a link connecting said punch and the free end of said arm so that said arm is substantially perpendicular to the axial plane of said punch when said punch is substantially at the start of its actual perforating movement,

and means to oscillate said arm in synchronism with the reciprocation of said punch and die cally and laterally reciprocating gypsum boardv punch comprising a power shaft substantially in the transverse vertical axial plane of the path of said punch, a bell crank having its fulcrum below said shaft and at one side of said plane and with its work pivot and power pivot operable in paths closely approaching a tangent to said plane, a connecting rod between said work pivot and said punch, a link connecting said power pivot to a crank on said powershaft, said elements and pivotal connections being so related that substantially all of the movement of said work pivot is above the horizontal plane of said bell crank fulcrum and said work pivot is closely adjacent said vertical plane when said punch is at the lower end of its vertical stroke, and substantially all of the movement of said power pivot is below said horizontal plane and said power pivot is closely adjacent said vertical plane when said punch is at the upper end of its stroke.

8. A machine for perforating gypsum board webs continuously moving in a horizontal plane, comprising a transverse row of vertically and horizontally reciprocating punches for perforating said web with transverse rows of perforations, a transverse crankshaft in a plane perpendicular to said web and substantially midway of the horizontal movement of said punches, a bell crank fulcrum shaft between said crankshaft and said punches, a power arm secured to said fulcrum shaft and having a link connection with said crankshaft so that the major arcuate movement of the power pivot of said arm is below the horizontal plane of the fulcrum, and work arms secured to said fulcrum shaft and each having a link connection with a respective punch, the link connected ends of said work arms operating in an are closely approaching a tangent with said perpendicular plane.

9. In a plasterboard perforating machine for a continuously moving gypsum board web comprising a reciprocating carriage, a punch and die on said carriage and mounted to enable said web to pass therebetween, means for reciprocating said carriage so that an intermediate portion of the stroke thereof in the direction of movement of said web is at the same speed as said web, a transverse crankshaft in a plane perpendicular to said web, and a compound link and lever transmission between said crankshaft and said punch to .cause a comparatively long stroke of said punch, said punch being free from said web during the major portion of said stroke, and said crankshaft movement and said transmission ,being related to the movement of said carriage so that only a minor portion of said stroke is used for the actual perforation and withdrawal of said punch, said actual perforating and withdrawal 'being accomplished when said punch is substantially in the said perpendicular plane of said crankshaft.

10. In a perforating machine for a continuously moving wallboard web having the usual punch and die in co-operating perforating relationship to said web, means to reciprocate said punch and die to travel at the same speed as said web during an intermediate portion of their forward stroke, a transverse driveshaft substantially in the transverseaxial plane of the path of said punch and die, a support for said punch comprising a piston reciprocable with said punch and die and substantially axially coincident with said plane when said punch is at either end of its perforating stroke, apunch operatingtransmission between said crankshaft and said plane and comprising a bell crank atone side of said plane, a connecting rod between the work pivot and said punch, and a link between said crankshaft .and the power pivot, said bell crank and said connecting rod and said link being pivotally related so that said punch and said connecting rod are substantially in axial alignment substantially in said transverse axial plane of said crankshaft at both ends of the vertical stroke of said punch.

11. In a perforating machine for a, continuously moving web having a horizontally reciprocating carriage adjacent said web arranged to move at the same speed as said web during a portion of each reciprocation, the combination of a plurality of punch guides on said carriage, individual punches respectively disposed in said guides for horizontal reciprocation with said carriage and for vertical reciprocation in said guides to punch said web, individual operating rods pivotally connected at one end thereof to each punch, bell crank means pivotally connected to the respective opposite ends of said rods, and crank means forsimultaneously operating all of said bell crank means to drive said rods and reciprocate said punches in: said guides in timedguides for horizontal reciprocation with said carriage and for vertical reciprocation in said guides to punch said web, individual operating rods pivotally connected to each punch, bell crank means connected to each of said rods, and means for simultaneously operating said bell crank means to effect reciprocation of said punches in said guides and provide a high speed penetration and withdrawal of all of said punches with respect to said moving web during each horizontal reciprocation of said carriage.

13. In a perforating machine for a continuously moving web having a horizontally reciprocating carriage adjacent said web arranged to move at the same speed as said web during a portion of each reciprocation, the combination of a plurality of punch guides on said carriage, individual punches respectively disposed in said guides for horizontal reciprocation with said carriage and for vertical reciprocation in said guides to punch said web, individual operating rods pivotally connected to each punch, continuously driven crank means for simultaneously operating all of said rods to reciprocate said punches vertically, and a shearing connection between each of said rods and said crank means, whereby each punch is individually protected against damage by engagement with objects of excessive hardness without interfering with the operation of the other punches.

' 14. In a perforating machine for a continuously moving web having a horizontally reciprocating carriage adjacent said web arranged to move at the same speed as said web during a portion of each reciprocation, the combination of a plurality of punch guides on said carriage, individual punches. respectively disposed in said guides for horizontal reciprocation with said carriage and for vertical reciprocation in said guides to punch said web, individual operating rods pivotally connected to each punch, means for vertically reciprocating said rods to reciprocate said punches in said guides during horizontal reciprocation of said carriage, the pivotal connection between each rod and each punch permitting horizontal movement of said punches, and a shearing connection between each of said rods and said reciprocating means.

15. In a perforating machine for a continuous- 17 moving web having a horizontally reciprocating carriage adjacent said web arranged to move at the same speed as said web during a portion of each reciprocation, the combination of a plurality of punch guides on said carriage, individual punches disposed in said guides, operating means disposed above said carriage including a rotatable crank shaft and bell crank means respectively iournaled in fixed bearings and conof a plurality of punch guides on said carriage,

individual punches disposed in said guides, operating means disposed abovesaid carriage including a rotatable shaft ioumaled in fixed bearings, individual connections between said operating means and each punch comprising telescoping members respectively connected to'a punch and the operating means, and a shearable pin normally preventing telescoping movement of said members relative to each other.

17. In a punching machine, a carriage mounted for horizontal reciprocation, a plurality of open ended cylinders on said carriage, pistons mounted for vertical reciprocation in said cylinders, punches respectively :removably supported-on the lower ends of said pistons, connecting rods individually pivotally connected to said pistons and extending from the upper ends of said cylinders, and common means for operating all of said connecting rods in timed relation to reciprocate said pistons in said cylinders, said common means comprising a constant speed crankshaft, and a plurality of bell crank means operated by said shaft and individually connected to said piston rods.

18. In a perforating machine for a continuously moving web having a horizontally reciprocating carriage adjacent said web arranged to move at the same speed as said web during a portion of each reciprocation, thecombination of a plurality of punch guides on said carriage, individual punches disposed in said guides, operating means disposed above said carriage including-a rotatable shaft Journaled in fixed bearings, individual connections between said operating means and each punch commising telescoping members connected respectively to said punches and op pivotally connected at its opposite ends to-saidwork pivot and said punch respectively, and link means pivotally connecting said power pivot to said crank.

20. An operating mechanism for axially reciprocating a laterally reciprocated punch in timed relation with the lateral reciprocation thereof, comprising a continuously rotatable power shaft, crank means on said shaft, a bell crank'having its fulcrum offset from the axis of said shaft, link means connecting said crank means to an arm of said bell crank to oscillate said bell crank as said shaft is rotated, and a connecting rod pivotally connected at its opposite ends to said punch and to another arm of said bell crank to effect axial reciprocation of said punch as said bell crank oscillates.

21. In a punching machine for a continuous ly moving web having a horizontally reciprocating carriage adjacent the web arranged to move at the same speed as the web during a portion of each reciprocation, the combination of a punch guide on said carriage, a punch disposed in said guide for horizontal reciprocation with said carriage and for vertical reciprocation in said guide to punch said web, continuously rotatable crank means, a bell crank having its fulcrum offset from the axis of rotation of said crank means, said bell crank having a work pivot and a power pivot, a connecting rod pivotally connected at its opposite ends to said work pivot and to said punch respectively, and link means connecting said power pivot to said crank to effect oscillation of said bell crank and reciprocation of said punch in said guide and provide a high speed penetration and withdrawal of said punch with respect to said moving web during each horizontal reciprocation of said carriage.

- 'I'EODORE T. YOUNGFELT.