US2961138A

US2961138A - Feed mechanism

Info

Publication number: US2961138A
Authority: US
Inventors: Anthony J Kaye
Original assignee: General Electric Co
Current assignee: General Electric Co
Priority date: 1958-12-30
Filing date: 1958-12-30
Publication date: 1960-11-22
Anticipated expiration: 1977-11-22

Description

A. J. KAYE FEED MECHANISM Nov. 22, 1960 Filed Deo. 30, 1958- Nov. 22, 1960 A. J. KAYE 2,961,138

FEED MECHANISM Filed Dec. 30, 1958 3 Sheets-Sheet 2 A. J. KAYE FEED MECHANISM Nov. 22, 1960 3 Sheets-5heet 3 Filed Dec. 30, 1958 United States Patent FEED MECHANISM Anthony J. Kaye, Schenectady, N.Y., assignor to General Electric Company, a corporation of New York Filed Dec. 30, 1958, Ser. No. 783,878 12 Claims. (Cl. 226-172) This invention relates to a stock feed mechanism for a punch press or the like, and in particular, to a mechanism which is capable of high feed speeds and great accuracy in positioning the stock.

In feeding a punch press or similar device, the stock must be repeatedly positioned in the work area of the press both at high speed and with great accuracy so that the various press operations may be carried out effectively. lPresent day stock feed mechanisms such as roll and hitch types have not been entirely satisfactory, primarily because they are relatively slow and inaccurate. Fundamentally all of these prior art devices fail to clamp the stock continuously and, as a result, at various times the stock floats (i.e., is not positively gripped). Hence, the momentum of the stock moves it past the desired location in the work area introducing positioning errors which result in spoilage and Waste of the stock and excessive wear of the dies.

To overcome this problem, attempts have been made to eliminate stock override by feeding short of the work area, releasing the stock and then aligning it properly by means of pilot pins located on the die. 'Ihis solution, however, has proved far from effective since it is apparent that clamping and unclamping of the stock prior to final alignment of itself introduces positioning errors. Concurrently, it also reduces, by virtue of the need for final alignment, the speed with which the press operates. In addition to the economic losses due to slow and inefficient press operating speeds, die costs are also increased since pilot pins or similar aligning instrumentalities must be incorporated in the dies to facilitate the nal aligning operation.

In order to overcome the foregoing difculties and provide a feed mechanism which is both accurate and rapid in its operation, it is contemplated to construct a feed mechanism wherein the material fed to the press is positively clamped during the entire operation.

Therefore, it is an object of this invention to provide a feed mechanism wherein material being fed to an apparatus is continuously clamped;

Another object of this invention is to provide a feed mechanism in which the material is continuously clamped and there is no relative motion between the material and the clamping and advancing means;

Yet another object of this invention is to provide a feed mechanism which accurately positions the material in the work area of the punch press without the use of pilot pins for aligning the material;

Still another object of this invention is to provide an intermittent high speed feed mechanism for a punch press or the like in which the material may be accurately positioned in the press work area by eliminating inertia override effects.

Other objects and advantages of the invention will become apparent as the description thereof proceeds.

`In one embodiment the advantages of the invention are realized by providing a feed mechanism having a multiplicity of clamping stations which are so actuated that each of the clamping stations in turn grips the stock and continues to do so until the succeeding clamping station is brought into engagement with and grips the stock. Hence, a continuous clamping overlap is maintained between suscceeding clamping stations and the stock is prevented from floating The novel features which are believed to be characteristic of this invention are set forth with particularity in the appended claims. The invention itself, however, both as to its organization and method of operation, together with further objects and advantages thereof, may be best understood by reference to the following description taken in connection with the accompanying drawings in which;

Figure 1 is a perspective view of the novel feed mechanism shown in conjunction with a punch press;

Figure 2 is a detailed side elevational View, partially broken away, of one of the feed mechanisms illustrated in Figure l;

Figure 3 is a plan view of one of the feed mechanisms of Figure l;

:Figure 4 is a sectional view taken along the line 4-4 of Figure 3;

Figure 5 is an enlarged sectional view taken along the lines 5- of Figure 3;

Figures 6 and 7 are diagrammatic illustrations of the indexing barrel cam and are useful in explaining the operation of the device;

Figure 8 is a perspective view of an alternative embodiment of the feed mechanism;

Figure 9 is a fragmentary elevation of the feed mechanism illustrated in Figure 8;

Figure l0 is a sectional view taken along the lines lll- '19 of Figure 8;

Figure ll is a fragmentary perspective of yet another embodiment of a feed mechanism;

Figure l2 is a sectional view taken along the lines 12--12 of Figure l1;

Figure 13 is an enlarged perspective of a clamping mechanism.

Referring now to the accompanying drawings in which like reference numerals denote corresponding parts throughout the several views, Figure l discloses a punch press indicated generally at 1 and having a frame 2 which supports a press bolster section 3. A plate 4 is fastened to the bolster section 3 and supports similar feed mechanisms 5 and 6 for moving an elongated strip of material 7 from left to right to the press work area, indicated generally at 8, where a die member 9 secured to a reciprocating cam 10, carries out the desired operations.

The feed mechanisms 5 and 6 are identical in construction and operation and the subsequent discussion Will be limited to a description of the mechanism 5 located to the left of the press. It will be understood, however, that the discussion applies with equal force to the corresponding mechanism 6. The stock feed mechanism 5 is so constructed and arranged that as any increment of the stock 7 enters the feed mechanism it is clamped and advanced towards the press 1, remaining so clamped until a succeeding increment of the stock has passed into the feed mechanism and is clamped thereby. To achieve the foregoing, the stock 7 passes between two

plates

11 and 12 which are free to rotate on a common shaft 13. The plates support a multiplicity of spaced clamping stations 14, 1S, 16, 17, 18, and 19 which clamp the stock and advance it toward the work area 8 of the press.

Each of the clamping stations includes a movable member 14a, 15a, etc., secured to the upper plate 11 as may be seen most clearly in Figure 2, and a cooperating xed member 14b, 15b, etc., secured to the lower plate 12. The movable clamp members are depressed, in Y Patented Nov. 22, 1960 a manner presently to be described, and cooperate with their respective fixed clamp member 14b, 15b, etc., to engage and clamp the stock 7. The fixed clamp members have projecting pins or lugs extending below the plate 12 which are driven to rotate the

plates

11 and 12 and advance the clamping stations and the material toward the work area 8 of the press.

' Positioned in the path of the clamping stations etc., and extending parallel to the direction of movement of the stoclzsN a stationary cam surface 20 fastened to' an L-shaped mounting bracket 21 which locks the clamping stations intorclam'ping relation with the stock. Upon counterclockwise rotation of the

plates

11 and 12 each ofthe movable 'clamp members 14a-19a successively passes underneath the cam 2t) which urges them down to grip thestock 7, clamping it securely.

As can be seen most clearly in Figures 2 and 4, which shows clamping station 17 beneath the cam surface 29, the movable clamp member 17a is urged downward into engagement with the stock 7. Upon rotation of the

plate members

11 and 12 the clamping station 17 remains beneath and continues moving to the right of cam 2i) advancing the stock in the same direction and remaining in clamping relation therewith during its entire passage beneath the cam..

The spacing of the clamping stations aroundthe periphery of the plates and the length of the cam is such that each individual station 14-19 in turn passes beneath the cam and remains in contact therewith until the succeeding station clamps the stock 7. Thus, the stock is continuously maintained in a clamped condition due to the overlap in clamping between successive clamping stations. Since the clamping stations move along with stock as it passes through the feed mechanism, there is no relative motion between the stock and the `stations eliminating inertia effects upon releasing the stocx.

In yorder to advance the material a predetermined amount with each operation of the press, a motion transmitting means is provided to actuate the feed mechanism by rotating the

plates

11 and 12 in response to each operational cycle of the press 1. A crank shaft fastened to the press eccentric, not shown, is secured to a connecting rod 22, the lower end of which is threaded and supported in `a rod end 23. The rod end 23 is provided with a pin 25 which supports a crank arm 26 mounted on a shaft 27. The rod 22 is reciprocated with each operation of the cam rotating, crank arm 26 and the shaft 27 during each press operation by a predetermined amount. The shaft 27, which is journaled in a suitable bea-ring mounted in bearing block 28, drives gears 3i) and 31 through a one way clutch 29 to transmit rotation in one direction only. Hence, the shaft 27 and the

gears

30 and 31 are driven during the press upstroke only to rotate a barrel cam 32 mounted on a common shaft with the gear 31, a predetermined amounty during each press operation.

The barrel cam 32 is so positioned that a helical groove 34 along the surface of barrel cam 32 intercepts the pins 14b, 15b, etc., to advance them a predetermined distance along the groove with each rotation of the barrel cam. As the pins move along the groove 34 the

plates

11 and 12 are rotated` moving the individual clamping stations along beneath the cam member 20, and advancing the stock toward the press. To insure that the clamping stations move linearly while beneath the stationary cam 20, movement of the pins 141)',V 15b, etc., along the helical ygroove of the barrel cam 32 is restricted by a pair of cam surfaces 35 and 36 (which may be seen most clearly in Figures 6 and 7) disposed directly above the cam 32 and form a linear guide which forces the pins to advance linearly while traversing the groove 34.

'However,` since the index pins are fixed to the plate 12 and tend to move in an arc with rotation of plate 12,

the center of the-rotating

plates

11 and 12 must be free to oscillate if the pins are to move linearly between the

cams

35 and 36. Hence, the shaft 13 supporting the

plates

11 and 12 is mounted on an arm 37 which is free to pivot about a pin 38 secured in a bracket 39 fastened to the press frame. The shaft 13 is journaled in the ball bearings 42 and 43 fixed to the pivot arm 37 to permit the plates, which are fastened together by bolts 41, to rotate about the shaft. A groove 40 in the arm 37 forms a passageway to permit the index pins to pass during each complete rotationof the

plates

11 and 12.

The manner in which the shaft 13 oscillates as the pins move between the

cams

35 and 36 is illustrated schematically in Figures 6 and 7. Thus, in Figure 6 the indexing pin 18b of clamping station 18 is Vshown approximately midway down the linear path defined by the

cams

35 and 36 `while the indexing pin 17b of the succeeding clamping station is approaching the left hand end of the barrel cani. With the shaft 13 located as shown, the indexing pins 18h and 17b tend toV move along the arcuate path indicated in the drawing by the legend are If the shaft 13 remains fixed, it is apparent from the drawing that no further. movement of the pin is possible since further rotation of the plates forces the pin against cam 35 preventing further'rotation of the barrel cam 32.

Consequently, the shaft 13 must vmove downwardly towards the cams until the chordal distance between the pins lies along the guide way, as shown in Figure 7, by the line bearing the legend chord, and the pins iare free to travel linearly. Since the pivot arm 37 is free to move, continued rotation of barrel cam 32V and the action of pin 18b lon cam 36, pulls `arm' 37 down, displacing shaft 13 as illustrated in Figure 7, until the chordal distance between Vthe pins llies :along the guideV way. -Thus, the pin 18h travels to the end of the passage 'and pin 17b is aligned with the opening between-the two

cam plates

35 and 36. The center of the

rotating plates

11 and 12 oscillates in ythe manner so that the indexing pins, the clamping stations and the stock 7 are advanced linearly by the feed mechanism toward the work area.

The lstructural ydetails of the clamping stations are illus trated in Figure 5. The movable upper kclamp member 15a of station15 includes a cylindricalmernber 44 having a tiange 45 which engages the underside of plate 11. A

ball thrust bearing 4.6 having a iContact surface 47 is secured to the lower vend of the cylinder 44 and clamps the stock 7 against a cooperating lower clamp member 15b whenever the cylinder 44 is displaced downwardly. A cap 48 retaining aball 49 is threaded on the upper end of the cylinder 44, so that the ball49 makes contact with the stationary cam member 20 forcing the cylinder 44 down against the action of a compression spring member 50 fastened between the cap and the surface of the plate 11.

The lower clamping member`15b also includes a bali thrust bearing "51 Vhaving a contacti surface 52 which cooperates with the corresponding surface 47 of the movable clamping member to hold the stock 7 An indexing pin or 1ug53 is rigidly fixed to the plate 12 by means of a set screw 54 and extends'below the plate 12 to engage the groove 34 inv the Vbarrel cam 32. Ball thrust hearings 46 and 51 are provided-so thatthe Contact surfacest47 and 52 will not rotate with respect lto the stock 7 as

plates

11 and 12 turn about shaft 13.l VThat is, 'as plates 11 and 12 'rotate about the shaft 13, carrying the clamping stations with it, the stations tend torotate about their own axes. Any such rotation, or tendencyto rotation, of the clamping stations will produce a corresponding rotation or tendency to Vshifty the'stocl; `7 out ofv alignment. The thrust ball bearings 46 and 51, however, permit the clamp-ing stations to rotate about a vertical axis relative to the

plates

11 and 12 so that contact surfaces 47 and 52 which grip the stock will not rotate with respect to the stock. Consequently, anypdanger of misaligning Ythe material due to rotational movement of the plates and the clamping stations is eliminated.

In operation, the reciprocating rod 22 driven by the press eccentric rotates the barrel cam 32 on each press upstroke through the one-way clutch 29. The index pin 18]: located on clamping station 18 has come into alignment with the groove 34 and moves into the groove and between

cams

35 and 36, as barrel cam 32 rotates. Movement of the pin into the groove 34 rotates the

plates

11 and 12 about shaft 13 bringing the movable upper clamping jaw 18a under the stationary cam member 20 urging it downward to grip the stock 7. Since the path of the index pin is captured between the

cams

35 and 36, further rotation of the barrel cam advances the clamping station underneath the cam 20 moving pivot arm 37 to facilitate linear motion of the clamping station.

As the clamping station 18 continues to move towards the right and approaches the end of the stationary cam 20 the index pin 17b of the succeeding clamping station 17 moves into the barrel cam groove and brings station 17 under the fixed cam 20, clamping the next portion of the stock before station 18 moves out from underneath the cam 20. Thus, the stock 7 remains continuously clamped and never floats since the succeeding clamping station has clamped the material before the preceding clamping station is released. On the next press upstroke the succeeding clamping station moves linearly underneath the fixed cam 20 and the sequence of operation is repeated to continue supplying stock to the work area of the press 1.

It is obvious from the description of the invention that the feed mechanism 5 may be adjusted to advance the stock any desired amount during each press upstroke by varying the length of the rod 22 and the angle of the crank arm 26. Furthermore, the ratio of

gears

39 and 31 may be adjusted to control the rotation of lthe barrel cam 32 and vary the degree the stock advances during each upstroke of the press.

As shown in Figure 8, the stock may be clamped and advanced -by utilizing continuous belts 'above and below the stock to perform the same function as the

plates

11 and 12,. Thus, a pair of endless metallic belts 60 and 61 positioned above and below the stock support a multiplicity of

upper plates

62a, 63a, 64a, 65a, 66a, 67a and corresponding lower plates 62b, 63b, etc., which, upon rotation of the belts 60 and 61, brings successive ones of the clamping plate pairs into engagement with the stock 7 to advance it from left to right towards the press working area, not shown. A pair of cam surfaces 69 and 7?, as seen clearly in Figure 10, 7are supported by a bracket 71 and bring the clamping plates into engagement with the stock 7 and advance it towards the press.

Motion is transmitted from the press to the belts 60 and 61 to advance the stock a predetermined amount with each press operation. The connecting rod 22, which as described with reference to Figure 1, is connected to the press eccentric, is reciprocated in synchronism with each press upstroke to rotate a crank arm 26 and a shaft 27 to which it is fixed through the one way clutch 29. Rotation of shaft 27 drives bevel gears 75 to transmit motion to

gears

77 and 78 which drive belt 61 in a clockwise direction. A pair of idler gears 79, only one of which is shown, are mounted on a shaft 82 and are driven by the belt 61.

A gear 80, mounted on the shaft 76, is also driven from the shaft 27 and meshes with a gear 81 to drive a shaft 83 to which it is secured. The shaft 83 supports gears 84 and 85 which drive the belt 60 in a counterclockwise direction. A pair of idler gears 86, only one of which is shown, are secured to a shaft 87 and are driven by the belt 60. The belts 6) and 61 and the clamping plates which they support are rotated to advance each of these clamping plates underneath cam members 69 and 70, urging them into contact with the stock 7 to advance it towards the work area of the press. As can be seen most clearly in Figure 9, the

spacing between the clamping plates 62a etc., is such that a multiplicity of the clamping plates are simultaneously under the cams 69 and 70 and there is a continuous clamping overlap between successive ones of the plates, and the material 7 is firmly and positively clamped at all times.

Each of the upper clamping plate members 62a, etc., as may be seen most clearly in Figure 13, includes a stem 110 which is slidably mounted in a cap 111 secured to a rod 112. A pin 113 fastened to the stem 110 is free to move in slots 114 in the cap 111 to permit downward movement of the cap when the rod 112 passes beneath the cam 69 to compress a pair of disc springs 115 positioned between the cap 111 and the belt 60. The disc springs 115 are of Well-known construction and include a pair of round tapered discs having a central passage for the stem 110. The springs act as pressure springs which are compressed by the action of the cam 69 and the cap 111 to urge the

clamping plates

62a, 63a, etc., into engagement with the stock.

Referring now to Figure 11, there is illustrated yet another embodiment which, though similar to that illustrated in' Figure 8, differs therefrom by the elimination of the continuous supporting belts 60 and 61. Thus, in the arrangement of Figure 11 a link chain 90 and a sprocket wheel 91 is actuated in a similar manner to that illustrated in Figure 8 to advance a multiplicity of clamping

plates

92a, 93a, 94a, and 95a secured to the individual links of the chain into clamping position with the stock to be fed to the press. Although, for simplicity of illustration, only one chain link is illustrated in Figure 1l, it will be understood by those skilled in the art, that corresponding chain link, not shown, supports the other left-hand ends of the

plates

92a, 93a, etc. Similarly, a corresponding chain drive arrangement, as may be seen in Figure 12, is positioned beneath the stock to facilitate clamping.

Each of the plates 92a etc., includes a stern 1x10 which slides in a cap 111 supporting a rod 112 which is adapted to pass underneath the cam member 69. The cap 111 contains vertical slots 114 which receive a transverse pin member 113 secured to the stem 110 which moves within the slot when the cap 111 is depressed during the course of its passage underneath the cam 69. A disc spring assembly 115 is mounted between the bottom of the cap and the underside of the clamping plate and is compressed by the downward movement of the cap 111 to maintain the plate firmly in engagement with the material.

The

clamping plates

92a, 93a, etc., are supported on flanges 103 .rigidly secured to the chain links of the chain 90. Fixed to each of the flanges 103 is a mounting pin 104 which extends through the plates 92a, etc. As the rods 112 pass underneath the cam 69 compressing the springs 115, the clamping plates slide along the pin 104, as may be seen most clearly in Figure 12, until they engage with the stock 7. In this fashion, the chain 90vis not' distorted as the plates engage the stock as they would if the plates were rigidly secured to the chain. A recess in the plates is adapted to receive the head of the pin 104 as the plate is moved into clamping position along the pins, thus presenting a smooth clamping surface to the stock 7. In this manner each of the individual clamping plates is secured to one of the links of the chain 90 and are sequentially brought into engagement with the stock without in any way deflecting or distorting the driving chain.

While a particular embodiment of this invention has been shown, it will, of course be understood that it is not limited thereto since many modifications both in the circuit arrangement and in the instrumentalities employed may be made. It is contemplated by the appended claims to cover any such modications as fall within the true spirit and scope of this invention.

' Whaty I claim as new and desire.. to obtainfby Letters Patent of the United States is: Y v Y l. In a mechanism for feeding material toY anrapparatus, the combination comprising feed means foriadvancing material toward the work area of the apparatus includY` ing a multiplicity of clamping means successivelyjengaging material entering said feed means; motion-transmitting means to actuate said feed means' in;respons'e` to each operational cycle of the apparatusY including means for contacting at least one of said' clamping means and. urging it into engagement with'the material'andj'positively maintaining the clamping means in'engagem'ent with said material during each operational cycleof said apparatus, each of said clamping means being fmaintained in engagement with said .material `until the. suc-x ceeding clamping means engages ithe materialY so that it is continuously clamped while being fed tothe apparatus.

2. In a mechanism for feeding material'toan apparatus for performing operations' thereon, the lcombination comprising a rotary feed means'including a"multiplicity of clamping stations successive cones jof which :are adapted to engage and'advancetheqmaterial `upon`1rotajtion of said feed means, motion transmitting'meansrifolr rotatably actuating saidrfeed means in response to each operational cycle of said apparatus and rotatingV succeeding ones of said stations into engagement :with Asaid material, said clamping stationsbeing so positioned and spaced that the succeeding clamping station'engages the material before the preceeding station releases saidY material so that the material is continuously `clampedwhile being fed to said apparatus.

3. In an intermittent feed mechanism for supplying an elongated material to an intermittently'operated apparatus, the combination comprising rotatable. plate means for supporting a multiplicity of. spaced clamping stations adapted to engage the material, contact `means to urge said clamping stations into engagement .with said material, said contactmeans extending in the direction of motion of said material to maintain said 'clamping stations in engagement with said material for a .predetermined distance and motion' transmitting means to rotate .said plate means in response'to each operational cycle kof said apparatus to bring the clamping stations successively into interacting position. withgsaid 'contact means to engage and advance said material during eachV rotation, said clamping'stations being'so'spaced'thateach station remains in engagement with said material'until .the succeeding clamping station is'brought into interacting position with said contact means whereby said material is clamped continuously by one 'of said stations.

4. In a mechanism for feeding material to an apparatus for performing operations thereon the combination comprising a rotating feed means including a multiplicity yof lspaced clamping stations adapted to be brought successively into engagement with land toV advance-the material to the operating area of said apparatus, Vcam means positioned in the path of-said stations'extending in the direction of motion of said material, motion transmitting means to rotate said feed means from said apparatus during each operational'cycle thereof to Vbring the clamping stations successively into'conta'ct withsaid cam surface causing them to engage and :advance .said material, said cam and said stations being so constructed and shaped that succeeding clamping stationsare brought into contact Ywith said cam means before the preceeding station loses contact with said cam so that said material is always positively clamped by `one of `said clamping stations.

5. In an intermittent feed mechanism for a reciprocating apparatus the combination comprising a rotating feed mechanism including a pair of spaced rotatable elements arranged lto have an elongated materialrpass therebetween, atmultiplicity of spaced clamping `stations n mounted on said rotatable elements,rsaid clamping stations cooperating to engage and advance said material,

., arranged that each clamping station remains in contact with said cam means at leastuntil the succeeding station comes in contact with said cam means whereby the material is always clamped by one of said stations.

6. In an intermittent material feed mechanism for a Yreciprocating apparatus, the combination comprising a pair of spaced rotatable plates arranged to 'have the material passtherebetween, a multiplicity of clamping stations mounted on said plates, each of said clamping stations comprising a movable contact member extending through and projecting beyond one of said plates and cooperating with a fixed member extending through and projecting beyond said other plate, cam means positioned to engageY said movable contact and urge it into engagement with said materialand said'xed member to clamp said material, intermittent motion transmitting means engaging the projecting portions oftsaid fixed contact members to rotate said plates during each reciprocation ofv said apparatus and bring theY corresponding movable contact into engagement with said cam means to clamp said material and advance it a given distance during each reciprocation of said apparatus, said clamping stations being so spaced that each station remains in contact with said cam means at leastuntil the succeeding station comes in contact with said cam means whereby the material is always clamped by one of said stations.

7. In an intermittent feed mechanism, the combina- Vtion comprising feed means for advancing material towards a work area, said feed means including a multiplicity of movable clamping means to engage successive portions of the material, each of said clamping means including an indexing pin, intermittent motion transmitting means to actuate said feed means including cam means to engage index pins of the individual clamping means to advance said clamping means a predetermined amount during each intermittent motion, and means to cause said clamping means to engage andv remain in engagement with said material until the succeeding clamping means engages said material whereby .the material is continuously clamped. Y

8. In an intermittent feed mechanismfor a press or the like, the combination comprising feed means for advancing material toward the work area of the press, said feed means including a multiplicity of movable clamping means including individual index pins to engage upon movement thereof successive portions of Vthe ymaterial,

Y motion transmitting means responsive to each operation of the press to actuate said feed means, said transmitting means including a barrel cam means having a groove ,t member adapted to receive the index pins of said clamping stations, the rotation of said barrel cam advancing said clamping stations a predetermined amount'during each operational cycle of said apparatus, and means maintaining a given clamping means inengagement ,-with .said material 'until the succeeding clamping means has been'brought'intoengagement withv saidtmaterial so that said-material is continuously clamped while Abeingfed to said press.

v9. In an intermittent feed mechanisml for a press or the like, the combination comprising alinear feed' means for advancing the material to the workV area* of the press including a pair of rotating plates between lwhich said-material. is adapted to pass, amultiplicityof `spaced clampingstations positioned on saidrotatingplatemeans, suc- .cessive ones of which are adapted to engagethe material upon rotation of said plate means, each of said clamping means including an indexing pin extending from said plate means, motion transmitting means responsive to each reciprocation of said press to rotate said plate means and bringing successive ones of the clamping means into engagement with said material, said motion transmitting means including a barrel cam having a helical groove therein adapted to receive the indexing pin from the individual clamping stations whereby rotation of said barrel cam advances said pin and the associated clamping means a predetermined amount during each reciprocation of the press, and cam means positioned in the path of the clamping means and adapted to cause each of said clamping means to engage said material upon being rotated into contact therewith, said clamping means being so spaced that each clamping station remains in contact with said cam means at least until the succeeding clamping station is rotated into contact with said clamping means whereby said material s always clamped while fed to the press.

10. The intermittent feed mechanism of claim 9 including means to produce linear motion of said material by causing said individual clamping means to move linearly while engaging said material.

11. The intermittent feed mechanism of claim 10 including cam means to restrain movement of said index pins in the groove of said barrel cam in a straight line.

12. The intermittent feed mechanism of claim 11 including pivotable means to support said rotating plate means whereby the center of said rotatable plate means is permitted to oscillate.

References Cited in the file of this patent UNlTED STATES PATENTS 977,146 Von Glahn Nov. 29, 1910 1,568,047 Bisey Jan. 5, 1926 1,765,419 Goss June 24, 1959