US1967558A

US1967558A - Material feeding mechanism

Info

Publication number: US1967558A
Authority: US
Inventors: Erik W Mikaelson
Original assignee: TREADWELL ENGINEERING Co
Current assignee: TREADWELL ENGINEERING Co
Priority date: 1932-04-05
Filing date: 1932-04-05
Publication date: 1934-07-24
Anticipated expiration: 1951-07-24

Description

July 24, 1934. E. w. MIKAELSON 1,967,558

MATERIAL FEEDING MECHANI SM Filed April 5, 1952 s Sheets-Sheet 1 225 lii July 24, 1934- E. w. MIKAELSON MATERIAL FEEDING MECHANISM Filed April 5, 1932 S'Sheets-Sheet 3 Patented July 24, 1934 UNlTED STATES MATERIAL FEEDlNG MECHANISM Erik W. Mikaelson,

Easton,

Pa, assignor to Treadwell Engineering Company, Easton, Pa., a corporation of Pennsylvania Application April 5, 1932, Serial No. 603,375

13 Claims.

This invention relates to feeding mechanism and more particularly to devices of this designation which are adapted to feed material to metal working machines at a controlled rate of speed.

The general object of the invention is to provide a novel and improved feeding device for metal working machines.

A more particular object is the provision of a feeding device for metal working machines or the like, in connection with which means are provided for varying the speed thereof in definite relatively large increments, and further means are provided for obtaining a much finer adjustment of speed between the speeds afforded by the coarse adjustments of the first named means, the latter means being adapted to be operated by the metal working machine itself.

A further object of the invention is to provide, in connection with a device of this type adapted to feed material to a metalworking machine having a predetermined cycle of operation, means for varying the speed of the feeding device by definite relatively large increments, and further means for varying the speed of the feeding device during a portion only of the cycle of operation of the metal working machine to obtain a much finer adjustment of the feed of material during a given cycle of operation.

In its preferred embodiment, the invention contemplates the provision of a feeding device for a flying shear of the type disclosed in my copending application Serial No. 530,989, filed April 17, 1931, in which the speed of rotation of the shear knives varies during portions of their cycle of movement in order to synchronize the linear speed of the knives and the material at the moment of cutting, although it is obvious that the principles thereof may be embodied in an arrangement for feeding a definite fixed length of material to any machine during a predetermined cycle of movement of that machine and for varying said length in very small wd definite increments.

In the exemplary embodiment illustrated, an ordinary change speed gear box is interposed between the feeding mechanism and the common driving means for the feeding mechanism and the shear, for obtaniing a rough adjustment of the speed of the feeding means, which may provide for variations in the length of material out in increments of about two feet. Also positioned between the feeding mechanism and the driving means is a differential mechanism which is operatively connected with one of the rotating shafts of the shear knives, whereby, during a portion of the rotation thereof, the speed of the feeding mechanism may be increased by smaller amounts to Vary the length of material cut by finer increments, such as, for example, as small as or of an inch, between the limits of adjustment of the gear box.

Thus the feeding mechanism may be adjusted to operate rapidly through a portion of the interval between cuts by the shear and more slowly during the time the knives are engaged with the material, this slower speed being, in the case of the shear illustrated, the linear speed at which the knives and the material are adapted to move in substantial synchronism. This synchronism between the linear speed of the knives and material' being fed is obtained in the manner fully described in my copending application and will also be referred to hereinafter.

It has been found that it is good practice to adjust the shear knives so that, at the moment of making a out, they will be running slightly slower than the feeding device in order to preclude the possibility of their pulling or exerting a tension on the material. This will permit'a very slight ex cess of material to be fed during the actual cutting time and will result in the formation of a slight buckle in the strip. To allow for this buckle, the invention contemplates the provision of a main feeding device located at some distance from the flying shear and an auxiliary feeding device disposed as closely as practicable to the shear and adapted to be brought into operation at least by the time the tail end of the strip of material has left the main feeding mechanism.

Further objects and features of novelty will be apparent to one skilled in the art upon a consideration of the following specification when taken in connection with the accompanying drawings in which one embodiment of my invention is illustrated by way of example.

In the drawings:

Figure 1 is a plan view of a flying shear and feeding mechanism therefor which comprises a preferred embodiment of my invention;

Figure 2 is a vertical cross-sectional View taken on the line'2-2 of Figure 1;

Figure 3 is an end view of the gear box included in the means for obtaining the coarse adjustment of the feeding speed;

Figure 4 is a vertical cross-sectional view taken on the line 4-4 of Figure 1;

Figure 5 is a view in side elevation of the shear end of the installation;

Figure 6 is adetailed cross-sectional View illustrating the driving pawl mechanism for effecting the differential drive, and taken on line 66 of Figure 1; and

Figure 7 is a similar View of the holding pawl mechanism taken on line 7'? of Figure 1.

Referring to Figures 1 and 5 of the drawings, the numeral 10 designates generally a flying shear of the type disclosed in my copending application Serial No. 530,989, to which reference is made for a complete detailed description of the construction and operation of the shear and its control mechanism. For the purposes of the present specification, a brief description of this arrangement will suffice.

The upper and lower shear knives 11 and 12, respectively, which carry cutting blades 13 and 14, are mounted in the housing or pedestal 18 for rotation in unison upon the upper and lower shafts 15 and 16, respectively. Outside of the shear frame or housing 18, the upperand lower shafts 15 and 16 are provided with intermeshing gears, the upper one of which is shown at 20. Further along, the upper shaft 15 is provided with a device, generally indicated by the numeral 22, for changing the phase of rotation of the shaft 15 with respect to the aligned shaft 23, from which shaft 15 receives its driving force. A housing 25 is splined to the end of the shaft 23, and a worm wheel 26, enclosed within the housing 25, is keyed to the end portion of the shaft 15. An extension 27 of the housing 25 is provided with bearings for a worm shaft 28 provided with the worm 29 which is adapted to mesh with the worm wheel 26. It will be readily understood that, by manipulation of the worm 29 by means of a suitable tool applied to the squared end of the shaft 28, the

shafts 15 and 23 may be offset from each other by a definite predetermined angular extent for a purpose which will be hereinafter explained.

Shaft 23, supported in the bearings 31 provided on a suitable base 32, is adapted to carry upon its end opposite to that which is operatively connected to the shaft 15, a counterbalanced crank 35. With this crank 35 is adapted to be operatively connected another counterbalanced crank 36 which is fixed on the end of a driving shaft 37. A crank pin 38 carried by the end of the crank 36 is adapted to carry a slide block 39 which is adapted to move back and forth in the slot 40 provided in the crank 35. It will be noted that the axes of drive shaft 37 and of shaft 23 are out of alignment, and it will be readily understood that, by means of the sliding crank connection just described, although shaft 37 is adapted to rotate at uniform angular velocity, the shaft 23 will be given a non-uniform motion. In other words, during a portion of a single rotation of shaft 23, it will be moving more slowly than during the remainder of the rotation, and it will also be apparent that by means of the device 22 the angular velocity of the shaft 15, and consequently of the shear knives 11 and 12 at the time of taking a cut, may be varied between certain maximum and minimum speeds for a given speed of the driving motor.

Drive shaft 3'7 is adapted to be operated by the motor 42 through the shaft 43 and gearing 44, 45, 46, and 47, this transmission means being mounted in the frame 50 as clearly shown in Figure 1. It will be understood that, by means of the mechanism just described, the linear speed of the shear blades 13 and 14 may be synchronized with the speed of the material being fed to the shear during the actual cutting operation without changing the general speed of the flying shear in revolutions per minute.

The flying shear is provided with a delivery table 55, and a feed table 56 which is adapted to extend from the main feed roll stand 57 to a point in close proximity to the shear. A short table 58 is provided for supporting the material in advance of the feeding mechanism as it is delivered from the roller table 59.

Within the purview of the present invention,

any suitable type of feeding mechanism may be employed such as a roller-leveller or straightener or the like, but in the preferred embodiment which is illustrated in the drawings, there is shown a feed roller device comprising the lower roller 66, which is carried in bearings provided in the stand 57, and the upper roller 61 which in operation is adapted to bear downwardly upon the strip of material to be fed. The roller 61 is provided with trunnions or an axle which is rotatably carried upon the end of the lever arms 62, one of which forms a part of the bell crank lever 63, fulcrumed at the ends of the shaft 64 which is carried by the stand or support 57. The vertical arm 66 of the bell crank lever 63 is bifurcated at its lower end as at 67, and the bifurcations are adapted to straddle the rod 63 upon which is carried the coil spring 69 for urging the arm 66 rearwardly and thus causing the roller 61 carried in the upper arms 62 to bear resiliently downwardly upon the material being advanced.

Since, in practice, it is sometimes desirable.

to have the material advanced to the shear at a rate of speed which is very slightly greater than the linear speed of the blades at the timeof making the cut so as to cause the strip of material to buckle slightly, the main feeding rollers mounted in the stand 57 are disposed ata considerable distance from the shear, and consequently when the tail end of the strip of material has passed these rolls, there will be nothing but the momentum of the material to continue its movement, and since this momentum would pradually decrease, an irregularity in the length of the last piece cut from the strip would result. To obviate this difficulty, an auxiliary roll stand 70 is provided which includes the lower roll 71, the upper roll 72, and the levers 73. For transmitting the.

driving force to the auxiliary feed rollers, beveled gears 74 and '75 are mounted upon the ends of the lower roller axles and are adapted to mesh respectively with the beveled gears 76 and 7 7 which are carried upon the ends of the longitudinal shaft 78 which is adapted to rotate in the

bearings

79 and 80 carried by the

stands

57 and 70 respectively.

It will be noted that, since the auxiliary feeding device mounted in the stand 70 is normally out of operation, the compression spring 82 carried by the rod 83 which is pivoted to the lower arm 84 of the bell crank '73 is arranged to urge the roller .72 in a direction away from the strip of material, while the arrangement in the case of the main feeding device, as has already been described, is designed to maintain these rollers in operative feeding position. As a means for releasing the main feeding device from operation by raising the roller 61 and for simultaneously causing the roller '72 of the auxiliary device to engage the material, there is provided the cylinder and piston devices 90 and 91, the

piston rod 92 of the device 90 being connected i whet-auxiliary: feeding device. i'Itvwill be readily -=understoodi ..that an: outward -movement of tthe piston rods 92 .and195leffectedzbymthe admission f as suitable-fluid such as :compressediair -toithe I 5: cylinders i90f1and 91satt'the; aproper: endsithereof,

will cause the disengagement ofthemain feeding sldevice and the engagement of: the iauxiliaryrone.

The-admission of -pressure .fluid to the cylinders :.of thefdevicestQOzand? 91v :may be effected :by any 110 suitable means: such -.as a1tripzmechanismcopersated by a finger 1: adapted to contact with tithe ma-terial, ,OI,-llfrid6Sl-18d, it; may be: accomplished imanually .by'. an operator. 1 In case the" finger-1250 isissemployed, it isza'dapted ..to: -:-open'-'. .theizcontacts :15 .;:251,=as;shown.i1r Figure: 5 and break. theielectric'al c circuit'abetween the :battery; 252 wand-the: solenoid 253. i'Ehe solenoid z253zis designed.v to. operate-the -valve meansl 254 'for :controlling the i-admission "and :exhaust v:of fluid ..pressure to l. the ecylinders 20I.90:and 91. When the solenoid;253'.: isi de-energizedi the. piston. 255 of Cthe: controlling cvalve sis .zintthe position. illustratediwhereincfluid;pressure i:is .exhausted from the cylinders. 90,. 91; through the;.pipingZ1256 by. means of the passageway 257 --inthe-valvel255. '-"-When the tail endof the st'rip :zofsmaterialL-1260 has .passedithe .fingerv250 the -:contacts 251 are closed, energizing the solenoid 253,:raising the valve :body 255xandcausingfthe :valve passageway 261 to permit admission-offiuid L :rpressure' :tothe piping 255 which will thenrelease ithe l-feed: roller'fil from the: :material. .and cause athe". feed:roller 12*.to1engage it ata zpointnearer zthecshear. Any:otherzsuitableii-mechanism may bertsubstituted. forithe: fluid: pressure. :device diswc'lose'd. withinthe scope oftheappended claims.

fFcr .driving the feed rollers; any suitable source :of power-maybe employed,..but, for the purposes of obtaining: a betterlsynchronizationbetween the feedingimeans .andthe flying shear, it is preferred 140 to 1 21156 nthe same. source or :.power, such as: the

-- motor142; for driving'zboth of these instrumentali- 2 ities.: :E'or E'flihlSZ-iDUIYDGSG -a shaft .100 vis coupled .totthe opposite endtofiithershafte3 from the'motor 42'. and.issadaptednto drive lthetshaft 101'. through v .the :beveled: gearing indicated at :102. o'I'hesshaft f. 1011 is operatively: connected: to. theiinputzshaft 103i-of1 the changei' speedigeariassembly .indicated generallyi. by-the numeral .105, bynmeans :of the -bBVE1d zgears :106:"';The :output :shaft -108 'r-of iltheichangei 'speed assembly; :iscoupled" with; the

2' input. shaft; 109 or the differential: transmission acdevicefiindicated" igenerallyrby the numeral 1.10, sand the .oxrtput; shaft 111 xof-ithe 'adifferen'tial: de wi ice isadapteditobe connected? to the-shaft? 112 which drives the roller of the main feeding idevice byimeans :ot' the cooperating .clutchsmem- .rbersi 115:.and 1 16;; .the. last-"named "member." being a :urgeduintoaengagement :Wi-th thefolutchcmember .1115 Jay zmeans of the i; coiled srspr'ing i1 117. ":The

.clutch::is;adapted :tohei'disengaged ibyimeansi of -thez fiuid lipressure -.:device '.120, :ithe1 piston 5.121

aof twhich.:is.t.adapted2 to ibe connected 1; the bifurcated-clutch operatingarm: 122: byimeansz-of .i'thelink. 123.

- Byamea-ns of the change speed gearing 105,ia coarse adjustrnent :of the speed izof l the "feeding 'mefchanism may be obtained .whereby.the'--=length of: "cut-of the material may be varied -in' -incrementsof,-"-f0rexample, two feet. For this pur- 5' i pose there-are secured to the input shaft 193 of this unit 'the -'gears l25, 126,127,-and 128- -of successively decreasing-diameters. In this em- 1 'bodimentonly' fourof' these gears-are shownybut 'it;will' be-readily understoodthat'anypracticable --number may be used. On the output shaft 108 zwiths their correspondingagears icarried l by zthe shafts 103 an'dalOBaand:that;.ttherefore;the rota- ;tion. of the input:..shaft;.103 willtbe impartedt to the output shaft? 108; ins. theiproper:ratiorxtovobstain .the basic .operating? speed wofthe feeding mechanism .whiehris nextnb'elow thev exact speed i'required'fforthe :desiredxlength: of zcutsof .the

material.

The 'diiferentialmechanism 110 .is providedifor .-obtaining.iainer adjustmentof the speedofz'fthe I feeding mechanismv-so'that. theilengthaof the *ma- 1 terialmut maybevaried by. much smaller. aincrements than the two foot..intervalszafiordedtby 'Ltheschange speed assembly 105, and,-.-as: will be understood fromxthe: followingf.description; these i further finer: variations in feedingispeed' are 'obta'inedby speedinglup' the feedrollersiduringz only vaportion of the cycle ofc-rotatiomof.thezknivesof theiiflying' shear" '10. Moreztspecifically, the tin-{1100 J creased: speed. of .the device" to secure: .th'easecondary. adj ustment is: accomplished'pduring .a'ipo'rtion of .the. rotation xoflthe'i: blades when they. arernot engaged .inicuttingea "strip. ofxmaterial. .In'. this .zmanner; the. basic 1 speed: may :beaadj listed: at the'q05 nearest two footsintervali below thexdesired2exact speed" by means of the: change. speed gearing-105, and: by adjusting the Idevice-I22; the? :linear speed -of1the shear knives .atftthe moment offimaking-ia cut may be 'broughtlinto ."sub'stantial'. synchronism *with-this basic-speed. 'lfheniitherrsped:lofffeeding during a portion. ofithe' rotationcoflthe' knives, when theyaare' out of contact Withthe-xmztterial, may be increased vin oifder to' obtairi-ath'e exactidesired length of: out :without' interfering with"the;1115 synchronism which is necessaryiduring the: actual cutting operation. a I This rmeansifor' obtaining thez'sfine .zadjustment offithe feeding speedswill'inow.be described. Up'on the inner end of thezinputjshaft loilofiithe difier- "entialjdevice' isasecured theibeveldgear 140, an'd the inner end ofithe eoutput sha'ftl 111' carries the beveled: 'gear 141. i'Planetary-i-or ridleriigears T 142an'd I43 carriedbythest11b;shafts 144and 145 are adapted to mesh-with? the beveledigears 14G mag; -andllll; Thea shaftsi 144:;aiidi-145aare rotatably mounted in bearingscarrie'd by therplanet carrier or bodypo'rtion- 1590f the;;diiff'erential.110; :When this bddy portion 150 is statio-nary,'.itiwillt be seen E that the output "shaft 111 WiIP'riJtate in a'idirec- 61: 0

ti on opposite to that of the input shaft lit-gyand at the same speed',---which lSydf coursefdetermined by thesetting of 'the'change speed-arrangement 105." It-will'also be understood-that rotation-of the -body-mernber 150 of the differential in thefi same direction-as the direction of'rotation" of the output shaft 111 "vv'ill-increasefithe speed ofthe putputshaft and therefore ofthe fe'ed rollers at 57. "J'Iherfore/finergradations of the-speed'of fee'ding w'ithin the two foot intervals aiTo-rded by the'changespeedgearing may readily be obtained "by the prpper -amount o1= movement, during-a "given-cycle of operation-of theshear, applied to thisibodymemb'er l50yandit ispr'eferred =in the present'embo'dimentto move "the bodymember 1 15 150 in"one directionpnly; namely, that bywhich the "'speed' of' the output shaft 111" and the feed -"ro'llersmay' be increasedfrom basic speed corresponding to the setting -on='the =change-=-sped "assembly. This' movement ofthe'-member- 1 50 is 150 accomplishedby means of the following mechanism. H.

' Upon the extended outer end of the lower shear knife shaft 16 is fixed the counterbalanced crank arm 160. This crank arm is provided with a slot 161 and the count-erweighted portion 162. A block 165 is adjustably disposed in the slot 161 and is adapted to-receive a pivot pin 166 for the connecting rod 167, the other end of which is pivotally connected as at 168 with the lever arm 169' which is secured to the rock shaft 170. The rock shaft 170 is rotatably mounted in the bearings 1'72 and 173 which are mounted in suitable supporting frames 174 and 175. The shaft 170 is preferably disposed in parallel relation to the input and output shafts ofthe differential device 110 and at a suitable point, preferably opposite the inputshaft 109, a gear sector is secured upon the rock shaft 170. I

By referring particularly to Figure 4 of the drawings, it will be seen that the body portion 150 of the diiferential mechanism 110 is provided with a sleeve-like extension 182 which. is adapted to surround the input shaft 109 and in which the latter shaft is adapted to rotate. Bearing bushings 183' and 184 are provided at the points of frictional contact between the shaft 108 and the sleeve 182. The sleeve 182 is mounted for rotation in the bearings 185 which are carried by one of the uprights 186 of the differential frame 187. A gear or pinion 190 is mounted for rotation upon the sleeve 182 and is providedwith the-bushing 191. Keyed to an extension 192 of the gear 190 is the ratchet arm 195 which is adapted to carry,

by means of a pivot pin 196, the two ratchets or pawls 197- and 198 which are adapted to engage with the ratchet teeth 199 formed on the ratchet wheel 200, which is rigidly supported by the differential'body member 150. Each-of the

pawls

197 and 198 is provided with rearwardextensions 202 which are in turn provided with-rods 203 which are adapted to pass throughv the upper overturned portion 204 of the ratchet arm 195 and the pawls are adapted to be urged toward engagement with the ratchet teeth by means of the coil spring 205. The gear sector 180' is adapted to mesh with the gear 190 and upon each downward oscillation thereof, caused by the rotation of the crank arm 160 carried by the shear knife shaft 16,'will move the gear 190 and the ratchet arm 195m a clockwise direction, as viewed in Figure 6. Then, by means of the ratchet and pawl device, this movement will cause the'body member 150 of the differential to move a predetermined degree in the same direction of rotation as the 'output' shaft 111.

During the upward movement of the sector 180 when the crank pin 166 is moving through the lower half of its orbit, the gear 190 and the ratchet arm 195 will move in a counterclockwise direction, as seen in Figure 6, and thepawls197, 198 will click idly over the ratchet teeth 199. In order to prevent the body 150 of the differential from rotating, during this reverse movement of the actuating mechanism, due to the reaction of the load and the friction of the bearings thereof, the following mechanism is provided. Another sleeve-like extension 210 is provided for the body member 150 and this extension is adapted to surround the output shaft 111 which is adapted to rotate in suitable bearing bushings 211 and 212. The sleeve 210 is mounted in a bearing 214 which is carried by the upright 215 of the differential frame 187. A ratchet wheel 21'? is secured to the extension 210 and is provided with teeth 218 which areadapted to be engaged bythe holding

pawls

219 and 220 suitably supported by the pedestal 221 and adapted to be urged into engagement with the teeth by means of the springs 222, all of which is clearly shown of the drawings. a

In order to regulate the extent of movement of the sector 180, and thus of the body portion 150 of the differential 110, means are provided. for adjustably securing the pivot block 165 at different distances from the center of rotation of the crank arm 160. As stated heretofore, the block 165 is adapted to slide in the slot 161 formed in the crank arm, and it is also provided with a threaded opening therethrough through which the threaded shaft 225, is adapted to extend. The ends of the shaft 225 are rotatably supported in the end walls of the slot 161 and the shaft is capable of being rotated by the application of a suitable tool to the squared end 227 thereof. A look nut 228 or other suitable means is provided for retaining the. shaft in proper adjusted position. It will be readily understood that, upon rotation of the shaft 225, the block 165 may be moved along the slot 161 to the proper position to obtain the desired throw of the. sector 180. It is obvious ithatwhen the pivot pin 166 is axially aligned with the shaft 16 there will be no movement of the connecting rod 167 nor of the sector 180 and the speed of the feeding rollersv will be exactly that given by the adjustment of the change speed gear assembly 105. When the block 165 is positioned at the outermost limit of its movement, as illustrated in Figure 5 of the drawings, the sector 180 and the ratchet arm 195 will then move through their maximum arcs, and it is preferred that this degree of movement be xsufficient to speed up the feeding clev'ice during tional revolution of the feed rollers during a single revolution of the shear knives-and will, of course, cause an increase of two feet in the length of material out. One edge-of the slot 161 may be graduated as at230 in very small intervals representing, sayy or of an inch increments in the length of material cut, and the device may be very readily adjusted to effect these variations in the length of cut by settinga mark in the block 165 opposite the desired graduation in the scale 230.

From an inspection of Figure 5- of the drawings, I

it will be seen that the relation of the crank'arm 160 and the shear knives 11 and '12 is such that, during the'eifective rotation of thecrank arm 160 through the upper half of its circle of movement, the knife 12 will be moving from its lowermost position to its uppermost position whereit is adapted to cooperate with the upper knife 11 to make a out. By means of this arrangement, the speeding up of the device to provide for the additional length of cut over the basic setting of the change speed gear 105 takes place during the last half of the cycle of movement of'the shear knives and that the feeding rollers have returned to their basic speed with which the linear cutting speed of the knives has been synchronized at the time the cut is made. Therefore, it will be apparent, that this fine adjustment of the length of material cut cannot interfere with the adjustment of the device 22 by which the speed of the in Figures 2, 4 and 7.-

circumference and that the ratchet wheels are,-

"the 1 ratios of the neon-'s:

' to thezi'bo'dy': 150 of the differentialg which; of

knives at the momntof cut is substantially-synchronized with thespeed ofthe material at that'- instant. Any; fixed phase relation of the crank:- arm 160 and theshear knife 12 may exist forthe purposes of thisinvention, which will ensure that"- no' movement ofthe differential :planet carrier 150 takes place during the time the shearknives are making a cut;

Therratehet teeth 199 and 218 in the wheels 200' and -217 are as closely.:spaced as practicable so that the amount of rotation may-be governed! toawithin very small degrees, and :the provision: of 4.

multiple pawlsof diiferentlengths as has been described will be effective: to further subdividethese divisions; A practicable example-will further? illustrate the operation. of this entire arrangement.

Letiit be: assumed that the orbit of-2theshearknivesislB feet in circumference, that-"the shaft? carrying-the driving crank :is rotating at the rate of i3ll rev'olutions per. minute andthat the proportiont-anderelative locations of the driving: crank and the driven crank: are such that the momentary linear velocity of the shear knives varies,"

iduring onecomplete revolution, between the limits of ia'maximum rate of 600 feet per minute andv aminimum ratei of 300 feet per minute with at mean rate-"of- 450*feet per minute. It ishalsoi assumedtthat'bymeans of.-the worm and worm wheel adjustment: between the variable speed mechanism and'th'ershear, thefpoint at which the shear :knives .comeinto cutting position has been:

in the assembly 105 is 10 to 10,.9-t0xl0y8 to 10,

and '7 tom, the output shaft 108maybe adjusted 270, 240or 210 R. the inputshaftlOQ of "the differential 110 to thepoutput'shaft 111 thereof,

to rotate at'the rates of 300, The ratio of the speed of whenthe planet carrier 150-isstationary, is 1 to l; Therefore the speeds of the feed rollers; operatively connected'tothe output shaft 111, which are obtainable by adjustment of the change speed "gearing .105, .are'300, 270, 240*or 210 R. P; This will' 'give' 'feeding speeds of .600, 540,450 "or" 4:20 feet'per'minute, respectively; and; since the shear makes 30 cuts per minute, the lengthslof cut obtainable by means of the adjustment of "the" change speed gear 105 are respectively; If the desired length of cut is, for example, somewhere between 18 and-20 feet, those gears-in the change speed gearbox 105 will be engaged which will givethe 9'to 10ratio, and the' to obtain the additional length reproper setting made by the sliding block 165in quired Will be the crank'arm explanation.

Assuming that thefeed rollers aretwo feet :1n

say; 96 inches in circumference-and are provided with 384r teeth spaced at 'onei'quarter inch intervals, each tooth advanced will atooth or 3 5 of an inch of differential body held stationary,- Intermediate Then, if it is assumedxthat four :sets of change speed gears" 20,118,- 16 and l i'feet,

160.- The obtaining of this latter:

fine adjustment will be clear from the-following speed gear for controlling. said rate':of'feed1ng-,

' of the machine, means driven" direct1y..:by saidbe 24 inchesdivided: by-384, or of an inch. With two p awls-ar-- ranged in staggered relation, the feed may; be" advanced inlintervals of one half of thewidth of the actuallength ofmaterial.-fed.- The segment 180 is preferably of 1 "sufficient angular extent to, give one complete turn course,- will effect a complete additional revo'lu' tionof i the feed rollers and 6l.- This,"of course, 7 increases the-totalincrement 0f feedi-r'ig to the point where-the next-higher'gear ratio'of the device'l05 will-be used,. starting with the settings of the: block 165 will give"any-length desired within 'the two' foot intervals;

It will be apparent that the pre'sent invention may be applied-"to other apparatus than the hying shear illustrated the exemplary embodiment; It will-also be understood that -variouschanges =and modifications may be madein this embodiment 1, without 1 departing from the scope 9U. of the invention as illustrated in the following claims. a

Having-thus described-the invention, what is claimed as -new and desired to be secured by Letters Patentis:

1. In a deviceof the class described, in combination, a metal-working machine, continuously operating feeding-mechanism bymeans of whichmaterial may be-fed= to said machine at a predetermined rate; driving means for 'saidfeedinglflol mechanism, transmission means operatively con-- necting said a driving means and saidfeeding mechanism,- meansforpositively applying" acoarse adjustment to said transmission mechanism independently of the other elements Of -the device for regulating-thearate of feeding-by definite increments, and separate means actuated bv said metalworking machineand operativelycon-' nected with said transmission means for-regulat-'- ing saidrate of feeding in response to: a fine ad- "not. justment.

2. Ina device of the class described, incombination,- a metalworking machine adapted to perform successive predetermined cycles of op-- eration, continuously operating feeding mech- 115,- anism by meansof which material may be fed to said machine at a predeterminedrate, driving means for said feeding-mechanism, transmission means operatively-disposed between said driving means-and said feeding mechanism; means for positively applyingla coarse adjustment to said transmission mechanism independently of I. the other elementsof said device for regulating-the rate of feeding by definite incrementsyand means actuated by: said metalworking machine and 125: operatively' connected with said transmissionmeans for regulating said rate of 'feeding in--re-"-- sponse to a fine adjustment, saidlastnamed means being operative onlyduring-a portion of"; said cycle of operation, Y 30:

3. In a device ofthe class described, in com-'- bination; a metal working" machine, feeding mechanism by means of which material may be fed 'to said machine at a--predetermined rate, common driving means for: said machine and 5; said 1 feeding mechanism transmission mechanism disposed between said' driving 'means and" said feedingmechanism and including a change and a differential device, means for 'positively w; applying a coarse adjustmentto said 5 change speed-gear independently" of I the other elements determined rate, common driving means for said machine and said feeding mechanism, transmission mechanism disposed between said driving means and said feeding mechanism and including a change speed gear for controlling said rate of feeding in response to a coarse adjustment and, a difierential device, means actuated by said metal working machine and adapted to affect said differential device to control said rate of feeding in accordance with a fine adjustment, and means operatively disposed between said driving means and said metal working machine for affecting said cycles of operation, said last named feed controlling means being operative only during a portion of each cycle of operation.

5. In a device of the class described, in combination, a metal working machine adapted to perform successive predetermined cycles of operation, feeding mechanism by means of which material'may be fed to said machine at a predetermined rate, driving means for said feeding mechanism, change speed gearing operatively disposed between said driving means and said feeding mechanism for controlling the rate of feed of said feeding mechanism in response to a coarse adjustment, planetary gearing also disposed between said driving means and said feeding mechanism, means connected to the planet carrier of said gearing and operatively connected with said metal working machine and adapted to be driven thereby during a portion of its cycle of operation to move said carrier to effect a change in said feeding rate in response to a fine adjustment, and means for adjusting said last named means.

6. In a device of the class described, in come bination, a flying shear, feed rolls by means of whicha strip of material may be fed to said -shear at predetermined rates to control the lengths into which said strip is out, driving means for said feed rolls, a change speed gear disposed between said driving means and said rolls for varying the linear speed of said rolls and thus the lengths of cut by definite increments, means for positively adjusting said change speed gear independently of the other elements of said device and separate change speed meansalso disposed between said driving -means and said rolls and actuated by said shear for varying said speed and length of out by smaller increments.

7. In a device of the class deScribed in combination, a flying shear provided with a shear blade, means for feeding material to said shear,

means for adjusting the operation of said shear and said feeding means so as to synchronize the linear speeds of said blade and of the material being fed at the moment of taking a cut, and means for varying the speed of said feeding means operable only during intervals between successive cuts by said shear, whereby the rate of feed and consequently the length of cut may be varied without affecting the synchronism of said shear and feeding means during said cuts.

8. In a device of the class described, inlcombination,'a flying shear provided with a shear blade, means for feeding material to said shear,-

means for adjusting the operation of said shear and said feeding'means so as to synchronize the linear speeds of said blade and. of the material being fed at the moment of taking a cut, means for adjusting the speed of said feeding means in definite steps to vary the lengthof cut by'coarse increments, means for increasing the speed of material may be fed to said machine at a pre-' said feeding means from one of said steps to another or to an intermediate rate of feed, said rate mechanism, a differential device comprising.

planetary gearing operatively disposed between said driving means and said feeding mechanism, a

pawl and ratchet device associated with the planet carrier of said gearing, a crank arm adapt ed to be driven by said metal working machine, a connecting rod adjustably connected with said crank arm, gearing operatively disposed between said crank arm and said pawl and ratchet device,

said device adapted to be actuated to move said planet carrier in one direction only to increase the speed of said feeding mechanism, and means for adjusting the connection between the crank arm and said connecting rod for obtaining the desired increased speed. v

10. In a device of the class described, in combination, a metal working machine, a device for feeding material to said machine at predetermined rates, said device comprising feed rollers disposed at a considerable distance from said metal working machine, which is greater than the minimum length of material to be fed, auxiliary feed rollers disposed in close proximity to said machine, and means for bringing said feed rollers into engagement with said material in alternation.

11. In a device of theclass described, in combination, a flying shear and means for feeding material to said shear at predetermined speeds to control the length of cut of said material, said feeding means comprising feed rollers disposed at a considerable distancefrom said shear, addi tional feed rollers disposed in close proximity to said shear and means for disengaging said first named feed rollers and for simultaneously bringing said second named feed rollers into engagement with the strip of material being fed, as the tailend of said strip passes a predetermined point.

12. In a device of the class described,.in combination, a flying shear, feeding mechanism by means of which a strip of material may be fed to said shear, driving means for saidfeeding mechanism including a change speed device for adjusting the speed of said feeding mechanism at predetermined basic rates of feed, whereby the lengths into which said strip is out may be'varied by definite coarse increments, driving means'for said shear including a device for synchronizing the speed of said shear with that of said feeding mechanism at the time a cut is being made without changing the average speed of said shear;

means operatively connected with the "drive for said feeding mechanism for changing the basic speed of said feeding means to alter the length of cut by finer increments, and means controlled by said shear for operating said last namedmeans only during tween cuts.

V 13. In a device of. the class described, in comportion of the interval'bebination, a metal working machine, feeding mechanism by means of which material may be fed to said machine at a predetermined rate, driving means for said feeding mechanism, change speed" between said driving 7 ing connection acting solely in response to the operation of said metal working machine to move said carrier to efiect a change in said feeding rate in response to a fine adjustment, and means for adjusting the amount of movement of said driving connection.

ERIK W. MIKAELSON.