US1933500A - Radial spindle chucking machine - Google Patents

Description

Oct. 31, 1933- J. J. SPRING RADIAL S PINDLE CHUCKING MACHINE Filed March 1, 1930 14 Sheets-Sheet 1 Oct. 31, 1933- J. J. SPRING RADIAL SPINDLE CHUCKING MACHI'NE 14 Sheets-Sheet 2 vwemtoz Filed March 1, 1930 Oct. 31, 1933- J. J. SPRING RADIAL SI INDLE CHUCKING MACHINE Filed March 1-, 1930 14 Sheets-Sheet a I E gnoentoz Oct. 31, 1933,

.J. SPRING RADIAL SPINDLE CHUCKING MAQHINE Filed March 1, 1930 14 Sheets-Sheet 4 Oct. 31, 1933. J. J. SPRING RADIAL SPINDLE CHUGKING MACHINE Filed March 1, 1930 14 Sheets-Sheet 5 a 861 GMMW Oct. 31, 1933- J. J. SPRING RADIAL SPINDLE CHUCKING MACHINE Filed March 1, 1930 14 Sheets-Sheet 6 Oct. 31, 1933. J. J. SPRING RADIAL SPINDLE CHUCKING MACHINE Filed March 1, 1950 14 Sheets-Sheet 7 vwwQoz MQ-W- Oct. 31, 1933. .1. J. SPRING RADIAL SPINDLE CHUCKING MACHINE Filed March 1, 1950 14 Sheets-Sheet 8 Oct. 31, 1933. J. J. SPRING 1,933,500

RADIAL SPINDLE CHUCKING MACHINE Filed March 1, 1930 14 Sheets-Sheet 9 /7 a-vwemtop Oct. 31, 1933. J. J. SPRING RADIAL SPINDLE CHUCKING MACHINE 14 Sheets-Sheet 10 Filed March 1, 1930 v0 5 m S 0 ilwuw- MUM- 4 a M 4 Kw x M 5 V w EL.

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Oct. 31, 1933- J IN 1,933,500

RADIAL SPINDLE CHUCKI NG MACHINE [Filed March 1, 1930 14 Sheets-Sheet ll $12919. 20 T 7 /55 SC /5@ avwemtoz Oct. 31, 1933; J. J. SPRING RADIAL SPINDLE CHUCKING MACHINE l4 SheetsSheet l 2 Filed March 1, 1930 anon 06oz W 7% vflww/ Oct. 31, 1933. J. J.- SPRING RADIAL SPINDLE CHUCKING MACHINE Filed March 1, 1930 14 Sheets-Sheet l 3 E @(bQ anoemtoz y/ 3391;; M

m RN WU WV mw mm @N QH is, in part, a continuation; 1

Patented Get. 31, 1933 t at T FFEQE SPXNDLE CHUCKENG MACHINE 1 .losephJ. Spring, Berlin, Conn.,assignor to The 1 Goss and lleleenwliiachinc Company, New" Britain, Conn, a corporation of Connecticut "Application March 1, 193th Serial No. 432,296

3% Claims.

One of the objects of this invention is to pro- Vide a chucking machine capable of handling relatively large work-piecesand so to construct the machine, that it will'be comparatively universal in its action, being adapted to perform either internal or] external operations (or both) at each of its tooling stations.

Another object is to provide common. means for synchronously rotating all of the Work spindles; to provide speed'change means for simultaneously varying the rate ofrotation of all of said spindles; to combine therewith means for giving to each tool an individual rate of feed and to provide individual ineansfor varying the rate of relative rotation between certain ones of said work-spindles and certain ones of said tools;

Afurther object of the invention" is to provide a simplified transmission for effecting rapid traverse and slow feeding movements of the tools, 1

and indexing movements of the work turret and simplified automatic controls. therefor, whereby allof those movements may be effected automa'ti cally in a predetermined cycle withcomparatively few elements. I

Stillanother object is to control itself and the other andto embody in the feed trains means whereby it will be capable of varying its own rate of action.

A further object is so to combine the various trains that normally theoperative cycle of the machine would be automatically repeated and to provide automatically actuated interference means, under the control of the operator, for

' bringing the machine to rest just prior to the vent any of the mechanisms getting'out of time Q due to s such interference.

A still further object of the invention is so to construct thefmachine parts'and the various transmissions that they readily may be assembled and to provide transmissionsmeans. in the nature of timing couplings, whereby each feed-cam may be timed individually with respect to its drive shaft.

so to combine the feed and index' trains that each is adapted partially viewed from the rear of the machinc.

(oi... ta-ea Anotherobject is to provide an improved pneu matically actuated turret locking means.

An object of the invention also is to provide a pneumatic counter-balance for one of the-camactuated elements of the machine tool. i

' Other objects and advantages will be in-pa'rt indicated in the following description and in part rendered apparenttherefrom in connection with the annexed drawings. i

To enable others skilled in the art so fully to apprehend the underlying features hereof that they may embody the same in the various ways contemplated by this invention, drawings depicting a preferred typical construction havebeen annexed as a part of this disclosure and, in such drawings. like charactersbf reference denote corresponding views, of which:-- v d I Figurel is a front elevation of a-radial spindle chucking machine embodying this invention. Fig. 2 is a right end elevation thereof. Fig.

a plan of Fig. 1. Fig. 4: is a sectionipartly in parts throughout all the, d

elevation) substantially on the line 4-4 of Fig.

1 showing the worl:spindle driving train. Figs. 5 and 6 are side and end elevations; respectively; of a portion of the-machine casing showing'a speed change mechanism, later to be referred to,

for varying the speed of rotation of all the worrspindles. Fig. 7 is a side elevation of a gear containing speed change gearing and actuating means therefor, for varying the rate of translation of the tool-heads, gear box also con-j taining mechanism to render the feed andindex mechanisms effective alternately. Fig. 8 is a right end elevation of the gear box illustrated in Fig. 7. Fig. Qis a section substantially on the line 9-9 of Fig. '7. 10 is a section substantially on the line l0-l(i of Fig 1. Figll is a section substantially on the line l1l1 of Fig. 8. Fig. 12 is a section substantially on the line 12-12;of

8 showing the drive one of the slide actuating cams, a portion of index control means and a portion of the alternately to render effectiveafast and a slew feed'train, all later to be described. Fig. 13 is a section substantially on the line 13-13 of Fig. 12 the parts being shown moved in the direction indicated'by the arrow approximately" ten degrees from the positions shown I in Fig. 12. 14 is a horizontal sectional view through the gear box and a portion of the machine frame showing the drive to the index shaft, a portion of the tool feed actuating'train and aportion of a feed control mechanism later to be described, said mechanisms being shown as is a vertical sectional view through the turret supportshowing more particularly-the indexing means for theturret and a turret clamping mechanism later to be described. 16 is a horizontal sectional view disclosing the turret in-" Fig."

loo

dexing mechanism and a turret locking mechanism later to be described, together with an automatically actuated control for said locking mechanism. Fig. 17 is a detail section on the line l71'7 of Fig. 16. Fig. 18 is a central vertical section through one of the main slides and one of the cross sides and their actuating means, all later to be described. Fig. 19 is a detail sectional view of an impositive driving coupling embodied in the index drive train. Fig. 20 is a section on the line 20-20 of Fig. 19. Fig. 21 is a central section of a timing coupling one of which is embodied in each of the three tool-head feed trains. Fig. 22 is a left side elevation of the timing coupling shown in Fig. 2. Fig. 23 is a right side elevation thereof. Fig. 2 1 is a development of the tool-head feed and turret indexing trains. Fig. 25 is a diagrammatic figure illustrating the spindle driving trains, the tool-head feed trains, the turret index trains, and the turret locking and clamping mechanisms. Fig. 26 is a diagrammatic view illustrating the relative timing of the turret lock, turret clamp, and turret indexing mechanisms. Fig. 27 is a diagrammatic view illustrating the main slide reciprocating cam in conjunction with the dogs which shift a clutch member alternately to render effective rapid and slow drives for said cam.

Referring more specifically to the drawings, the invention is disclosed as embodied in a chucking machine comprising a substantially T-shaped main frame or base 1 affording at its extremities,

tooling stations indicated generally as L, M and N, each of which is adapted to be provided with one or more tools. Intermediate the tooling stations the base supports a turret K within which are rotatably journaled four equally spaced and radially disposed rotating worl -spindles 2, each carrying, at its outer end, a suitable work-holder or chuck 3.

As clearly shown in 3 there is one more work-holder than there are work-stations, thus, during the machining operations, one work-holder will always be located between the tooling stations N and L. This idle position is used as a loading and unloading station at which the operator is located to place the unfinished work-pieces in the work-holders and to remove the finished work-pieces therefrom after they have been machined.

Stated briefly, the present machine includes the following mechanisms:

(a) Spindle rotating mechanism,

(1)) Feed and traverse mechanism for tool slides,

(c) Turret indexing mechanism,

(11) Turret lock,

(6) Turret clamp; and suitable controls for all of said mechanisms.

For convenience, these mechanisms will be described in the order named:

Spindle rotating mechanism (Figs. 1, 4, 5, 6, l5 and 25) As shown in Figs. 1 and 1-, the turret K is journaled in and supported upon a ring a, secured upon a central upstanding part 1' of the base 1. Within the turret are journaled, as in bearings 5, the rotatable work spindles 2 previously referred to. Power to rotate the spindles 2 is derived from a motor 6 mounted on the machine frame as shown in Figs. 1 and 3. This motor is connected by a chain 7, or other suitable trans mission (see Fig. 25) with a shaft 8 journaled in an upstanding portion 1 of the main frame 1.

A bevel gear set 9 connects the shaft 8 with a shaft 10 also journaled in the frame portion 1 and which, as shown in Figs. 5 and 6, has one end extending exteriorly of said portion and has removably secured thereto a gear 11. This gear meshes with, and drives, a gear 12 removably secured upon the exposed free end of a shaft 13 also journaled in the frame portion 1 The gears 11 and 12 are in the nature of pick-off gears and may be removed and replaced by others having a different ratio, thereby to vary the speed ratio between the shafts 10 and 13.

Splined to shaft 13 is a gear unit 14 providing gears in and 14 adapted selectively to be meshed with complemental gears 15 and 15 on a shaft 15 journaled lengthwise of the machine frame, A hand lever 16, and arm 16 actuated thereby, serve to shift the gear unit 14 selectively to mesh said gears.

' The shaft 15 extends to within the upstanding portion 1. of the machine frame and carries at its forward end a bevel gear 17 which drives a similar gear 18 secured upon a short vertical shaft 19, journaled in a bearing bracket 19 secured to a portion of the main frame. A gear 20 fixed upon the upper end of the shaft 19 drives a gear 21 fixed upon a shaft 22 journaled, at oneend, in the bracket 19 and adjacent the other end in the turret K. To the upper end of shaft 22 is secured a gear 23, which meshes with and. drives four gears 24, each of which carries a bevel gear 25 which in turn serves as a driver for a similar gear 26 fixed to a shaft 27 journaled in the turret K. A gear 28, also secured upon each of the shafts 27 is maintained permanently in mesh with a gear 29 provided by a spool 29 rotatably and translatably journaled on each of the work spindles 2. Each of the spools 29 affords also a friction clutch element 30 and a tooth clutch element 31 adapted selectively to be engaged respectively with a friction cone 32 and a tooth clutch element 33 both fixed upon the work spindle 2. A fork 34 engaging the spool 29 is secured'upon an endwise movable rod 3% journaled in the turret. Clutch actuating levers 35 journaled in brackets 35 supported by a turret cover plate 76, have portions engaging the slide rods 3% selectively to engage the friction and toothed clutches. In the operation of the machine, after placing a work-piece in one of the chucks, the operator first pushes the lever forward to the position indicated by the dotted lines 35 (Fig. 4) This connects the friction clutch element 30 on the continuously rotating spool 29 with the then stationary clutch element 32 fixed to the tool-spindle, thus, starting the rotation of the spindle and work-piece impositively and without shock and undue strain on the spindle drive. After the spindle has attained a substantial speed of rotation the operator pulls the lever 35 to the position 35, thus, shifting i r the spool inwardly and engaging the toothed clutch elements 31 and 33. Thereafter the spindle is rotated positively.

From the foregoingit will be perceived that all of the work spindles are rotated in the same direction and at a common speed, which speed, however, may be varied as hereinbefore explained.

TooZ slides and actuating means therefor To effect relative bodily movement between the work-piece and the tools adapted to operate thereon, tools, located at the tooling stations L, M s

and external, on various forms of work-pieces, it.

has been found advantageous to provide at each tooling station a plurality of tool supports. These supports are adapted to carry the tool'required to perform the desired operation on the workpiece being machined. The machine is illustrated as providing, at each tooling station, a main slide MS fitted to move horizontally toward and from the work on guides 36 (see l3) At the'stations L and N the guides 36 are-provided by upstanding portions 1 of the main frame, but atstation M; for'convenience of manufacture, they are providedby a subfraine orgear-box GB supported upon the main frame and housing certain mechanism later to bedescribed; The gear-box is in effect a portion of the main frame and may be so considered. Each of theinain slidesis given reoiprocatcry motionfrorn a earn 38 secured .upon a supporting drum 38 carriedby'a rotary shaft iQ journaled respectively in the upstanding por-1 tions 1 and in the gear boX'G-B; A camgroove 38? formed in each of said cams is tracked by a roller 33 carried by. an arm 38. depending frorna slide 38 having an adjustable connection with The cam 384s preferably made of two semi-cylindrical sections 38 and'33 rernovably secured to a drum 38 asshown in Figs. 13 and 18. These sections may be removed and replaced by others attending a different cam groove, should the nature of the operation t be performed make this desirable.

An adjusting screw 39, journaled in an upward extension of slide 38 is threade'dinto main tool slide and affords means for manually adjustingeach'rnain slide toward and frorn'the workpiece and relative to its actuating cam.

Each main slide is provided at its upper side With a seat having therein a plurality of T-slots t adapted to have secured thereto any suitable form of tool-holder. Inasmuch asthe-tool-holder and the'tool oarried'thereby may beconventio'nal and form no part of this invenii'on'detailedillustration and description thereof is deemed "unnecessary.

For certain operation, such,-- for example, as drilling, boring and reaming, it may be desirable to produce, between one or more of the toolsand the work, a speed of relative rotation either faster or slower than'the speed at which all of the work spindles are rotated. To that end, each of-the main slides is preferably provided with a bore 1) within which may bejournaled a tool spindle 8 adapted to carry a suitable tools. In Figs. 1

and the main slide at the station L is'shown as fitted with a rotary tool spindle. -The mainsiides at the stations M and N may also be so fittedif the nature of the operation to-be formed at these stations demands it.

1 To enable the tool cpindle-tobe-ro-fated either in the direction of, or in opposition to, the direction of rotation of the Work spindle, thereby either to decrease or increase the rate of relative rotation between the work' and the tooLindividual variable speed reversible motors m may be-securedupon brackets m fitted to seats mlprovided by each of the main slides. The motors in are each connected by a chain m or other sui able transmission, with a. transverse. shaft m journaled in the bracket m which shaft isconnected, as by a worm and worm-wheel, with the .rnay carry tools.

tool. spindle 3; Conventional means (not shown) is provided for controlling the speed and direction of rotation of the motors m. I

Certain machining operations require the use 'ards do are removably secured upon seats provided by the main frame and .the gear-box. Reciprocatory movements are given to the crossslides by a rotary cam 41 having a cam-groove 41 tracked by a roller 42 journaled on'astud 42 carriedoy the cross-slide. The cam e'l is preferably made of two semi-cylindrical portions 41 and 41 (similar to those of cams 38) which are secured upon a sleeve 43 journaled in abearing 44 supported by the standard ii). A cain drive shaft 0 journaled in the standard so extends upwardly through the sleeve &3 and is connected to the sleeve by timing coupling as similar to that disclosed inFigs. 21, 22 and 2 later to be described.

A gear as on the lower end or each shaft 0 serves to transmit rotation to shafts.

To reducethe load on the crossslide cams 41 and thereby reduce wear on the cam grooves 41 and rollers 42, pnetunatic nieans rovided' for sustaining the weight of the cross-slides and the parts carried thereby. Thisis effected by forniing'i n the cross-slide a vertically disposed cylinder al into whi 1 isntted a piston 41 fixed to 'a'rod 413 which rests upon alportion of the standard 40. All pressure is admitted into the upper end of the cylinder as through a pipe 41 Sufficient air pressure applied between the end of the piston and the cylinder end wall'to substantially support the weight of the cross-slide its attached parts there's I substantially balancing the cross-slide. therefore, required to exert only a relatively slight pressure on the roller 42 to move the cross-slide either upwardly or downwardly. 7

Any .bie tool be carried by the cross-' slides CS and these tools may work independently of or in eonjunctionwith the tools carried by the main slides. Gneforrn of tool-holder and tool 21) is illustrated inFig. l8 and station M in Fig. 3.

It is to be understood, however, that other forms 1 of tool-holders and tools be substitutedand that the cross slides at the stations L and N also Power to rotate the came 38 and 41 is provided by a motor mounted on a suitable portion of lhe camgroove 41 is, I

the machine frame. This motor is connected by av chain 48 or other suitable transmission, with one end of a shaft A journaled in the gear-box C'B supported upon the rearwardly extending portion ofthe main frame, adjacent thetooling station M. The opposite end of the shaft A carries a gear 49 which drives, through an intermediate gear is, a gear 50 rotatably journaled on a short shaft a secured in the gear-box. A spool 51 rotatably and translatably mounted on the shaft'a provides a toothed clutchelement 51 adapted to engage a toothed clutch element 50 integral with the gear 50, anda gear 51" permanently in mesh with a gear 52 fixed upon a shaft R also journaled'in the gear-box. The shaft R a bevel gear 53, which drives a similar gear 53 secured upon a shaft B. Power may be taken from the shaft 13 through either of twotrains, thereby to rotate the tool-slide feed-' 'cured at 74 upon one end of a shaft I) also cams 38 and 41 either at a rapid rate to effect rapid traverse of the tools to and from the work orat a slow feeding rate during the machining operation. For convenience, one train maybe considered the main transmission and the other a supplemental transmission. The rapid traverse train will be described first.

Rapid traverse for tool slides Rotatably journaled on the shaft B is a gear 54 permanently in mesh with a gear 55 rotatably mounted on a shaft F journaled in the gear-box. A clutch spool 56, splined to the shaft B, provides toothed clutch teeth 56 adapted to be engaged with similar clutch teeth 54 integral with the gear 54. A similar clutch spool 57 splined to the shaft F has clutch teeth 57 adapted to engage clutch teeth 55 carried by the gear 55. Thus when the clutch elements 56 and 5"! are shifted to the left in Figs. '7 and 11 and upwardly in Figs. 2%. and 25, rotation will be transmitted to the shaft F at substantially the speed of rotation of the shaft B. A gear 58, fixed upon the shaft F drives a gear 59 secured upon shaft G, also journaled in the geanbox. A firstbranch line feed shaft P, journaled in the gear-box transverse to the shaft 6 and driven therefrom by bevel gears 60 and 61, carries a first worm 52 which meshes with and drives the cross-slide driving gear i6, and a second worm 63 meshing with a worm-wheel 64 fast upon the main-slide camshaft Q.

Journaled lengthwise of the main frame lis a shaft S, (see Figs. 3, l, ll, 24 and 25) connected by bevel gear sets 65 and with second and third branch line feed shafts P and P sir ilar to shaft P extending beneath the tooling stations N and L respectively. Each of these shafts also has secured to it a cross-slide actuating worm 62 and a main slide actuating worm 63 connected to actuate said slides as hereinbefore described. The shaft S is driven from the shaft G by spur gears 67 and 68 and bevel gears and "10.

With the clutch elements 56 and 5'? engaged with the clutch teeth 5% and 55 rapid rotation will be transmitted to the cams 38 and il located at each of the tooling stations and this rapid rotation is employed rapidly to translate the tools to and from the work-pieces. These rapid movements are highly desirable inasmuch as it reduces, to a minimum, the time required for the working cycle.

Slow feed for tool slides As hereinbefore stated, rotation be transmitted from the shaft 33 to the shaft F at a re duced rate and thence to the tool slides to give to the tools a relative slow feeding movement during the tooling operation. This is effected as will now be described. Removably secured upon the shaft B, exteriorly of the gear box is a gear '71 which drives a gear 72 journaled on a stub shaft '72 secured in the gear-box. Removably secured to the gear 72 is a gear '73 which drives a gear 74-. removably and frictionally sejournaled in the gear-box. The gears 7l72 and 7374 are in the nature of pick-off change gears and may be removed and interchanged with others having a different ratio. Adjacent the other end of the shaft D, the e is secured a relatively small gear '75 which drives a larger gear '76 forming a part of a gear unit '76 rotatably journaled on a stub shaft E and affording also a smaller gear 7'7. This latter gear drives a larger gear '78 forming a part of a gear unit "79 rotatably journaled on the shaft D. A smaller gear 80, also provided by the gear unit 79, is

permanently in mesh with a relatively large gear 81 rotatably journaled on the shaft F. Integral with the gear 81 is a toothed clutch portion 82 adapted to be engaged by a toothed portion 57 of the clutch element 57 previously referred to. From the foregoing it will be perceived that with the clutch element 56 shifted to engage the clutch teeth 56 and 54 and the clutch element 57 shifted to engage the clutch teeth 57 and 5% rapid rotation will be transmitted to the shaft 13, whereas by leaving the clutch teeth 56 and 54 engaged and shifting the clutch element 57 to engage the clutch teeth 57 and 82 slow rotation will be transmitted to the shaft F. The speed of rotation of the feed cams, and thereby the speed of translations of the tool slides, is proportionate to the speed of'rotation of the shaft F. The frictional mounting of the gear 74 comprises a safety device for the feed train.

The power drive'from the main feed shaft A to the feed drive trains may be interrupted by manually shifting the spool 51 to the left (Figs. 10, 14 and 24), thereby disengaging the clutchteeth 50 and 51 For this purpose a feed control lever Y is located at the front of the machine. This lever is fixed upon one end of a shaft y having at its other end an arm 1 connected by a link y to a similar arm g secured to a shaft 1/ journaled in the gear-box. A clutch shifting fork g is secured upon the shaft 1 and engages the spool 51 to move it axially.

Hand feed and index Manual means also is provided for actuating the feed trains and turret index. This means comprises a shaft X extending to the front of the machineand having a squared end adapted to receive a suitable actuating crank, not shown. On the inner end of shaft X, there is secured a bevel gear m which meshes with a bevel gear .10 rotatably journaled on the shaft a. Fixed to gear .10 is a clutch element affording clutch teeth :0 adapted; to be engaged by clutch teeth 51 provided by the spool 51. The lever Y and the parts connected therewith, also serve to shift the spool Turret indexing mechanism As hereinbefore stated, the work turret K is periodically indexed to carry a work-piece from the initial or loading station successively to the tooling stations L, M and N and thenceback to the initial station where the finished work piece is removed from the chuck. Each of these ninety degree movements of the work turret is effected by a two-stage index movement produced by an improved Geneva index mechanism comprising a slotted disk 83 secured to the underside of the work turret and having radial slots 83 formed therein. These slots are engaged by rollers 84 and 84 carried by a rotary disk 84 which is given one complete rotation for each ninety degree movement of the turret. The rollers are so located on the disk 84, that they are not on diametrically opposite sides of the axis thereof. This produces a continuous movement of the tur ret, after which the disk 84 has a further movement for a purpose later to be explained.

Power to actuate the indexing mechanism may be obtained from any. suitable source butpreferably it willbe taken from the tool-feed trainjas shown in Figs. 24 and 25. To that end, there is rotatably journaled' on the'shaft Ba gear adapted, at certain times, to be secured to said shaft by the clutch spool 56, clutch teeth 56 of said spool being adapted to engage similar teeth 85 formed on the hub of the gear 85. This gear drives a gear 86 fixed adjacent one end of ashaft J jou'rnaled in the gear-box, which shaft carries adjacent its opposite end a gear 87 connected by gear 88 with a shaft I having itsrear end journaled in the gear box. The forward end of the shaft 1 is fitted within a sleeve 89 journaled in a bearing 90 provided by the mainframe (see Fig. 19). A slip coupling SC, later to be described, intervenes between the shaft I and the sleeve 89. A.

gear 91, secured upon the sleeve 89, drives'a gear 92 fixed to ashaft 93 journaled in the main frame and upon this shaft is secured a Worm 94 which drives a worin-wheel 95 fixed upon a shaft/96, to whichthe index disk 84 also is secured.

Turret lock To accurately locate the turret and to insure against its accidental movement during the machining operation a turret-locking mechanism is rendered efiective after each complete indexing movement of the turret. This mechanism comprises a lock-bolt 9'7 slidingly fitted in a guideway 97 provided by the ring 4. The forward end of the bolt is tapered as indicated at 97 and this tapered end engages similarly shaped notches 9"] formed in the periphery of the disk 83. One wall of eachnotch 9'7 and the complemental wall of the lock-bolt are arranged substantially radial to the disk 8%. The opposite walls of the notch and lock bolt areat a substantial angle to said radial retbut merely necessitates a, slightly greater movement of the locking bolt; The lock-bolt 97 preferably actuated by fluid pressure and its movements are automatically controlled in timed relation with the indexingmechanism. A diiierential fluid-pressure motor W having relatively large and small cylinders '11) and we (see Fig. 16), separated by a partition w", contain similarly large and small pistons 10 andw respectively. These pistons are secured to a piston rod to and the cylinders are supported by the ring 4 adjacent the rear end of thelock-bolt. The pisi tons are connected with the lock-bolt by any suitable means, such for example as'by the connec-.

tion 97 shown in Fig. 16. v A fluid pressure line'98 is permanently connected by a port to with the smaller cylinder 20 at a point between the'partition 10 and the piston 10 whereby the fluid pressure in the cylinder w constantly tends to retract the lock-bolt. The fluid pressure line is also con-- ports 20 and 20 into the large cylinder 112 between the piston w and the partition w Thereupon the pressure on the-larger piston overcomes thepressure'on the smaller piston and advances By reasonof this construe-i the lock-bolt into locking position; In another position of the valve 10 a cylindrical portion w -"1 of the valve closes the port 1.0 and opens an exhaust port w whereupon the cylinder '11: is opened to the atmosphere and pressure in the. cylinder 20 behind the piston 20 retracts the lock-'' bolt. i

A spring 99, enclosed in the valve casing, nor-' mally tends to shift the valve inwardly-to the position shown in Pg. 16. To effect automatic actu ation of the vin tiined relation with the indexmechanism the inner end of the valve stem is through a guide 100 and carries a roller 101 which tracks the'periphery of the index disk -l cam 101 on the periphery of the disk- 84 a ts upon initial. movement of the disk, to force the valve outwardly in opposition to the spring 99 to effect retraction'of the lock-bolt. Near the end of the indexing movement of the disk 84, thev rollerlOl rides down the incline 101 and thereby the valve is shifted to the position which causes thelock-bclt to be advanced. The valve 10 also may be retracted manually by 'thehand grasp g should circumstances require it.

Turret clamp To insure absolute rigidity during the machining operations, this invention provides means rendered operative aiter each indexing of the turret; for clamping the turret to a stationary part of the machine. This is preferably effected by a clamp c of annular form com-' prising two semi-circular members 0- and 0 .(see Figs'S, i and 15) hinged together at c and, having inner V shaped grooves c with' walls diverging'outwardly to receive and cooperate with opposed annular tapered flanges 0 and 4: provided by the turret K and ring l, respectively. 7 The clamping ring members surround the flanges k and 4 peripherally and the tapered Walls of the grooves embrace the. tapered flanges laterally. The ring members are adapted to be constricted about the tapered flange Walls thereby to force the lower horizontal seat 70 of the turret down upon the. upper horizontal seat l of the ring 4 and to clamp the ring and turret against relative movement. Contraction of the ring members is preferably effected by a right and left threaded screw 0 having its opposite ends threaded into ears c projecting from said ring members. The screw 0 is rotated, to open and close the clamp c, in timed'relationwith the turret indexing mechanism. To that end a cam groove c formed in a drum c fixed to the turret indexing shaft 96, is tracked by a roller 0 carried by one end of a lever 0 fulcrumed at e in a bracket 0 supported by the main frame.

The other end of the lever 0 is connected to one end of a link 0 whose other end is con nectedwith an arm 0 fixed to the screw 0 Traverse, feed and index control mechanism As hereinbefore pointed out, the turret indexing, train and tool-feed train are --alternately rendered effective by shifting of the clutch spool 56 alternately to engage the clutch teeth 55 Each ofthese two trains actuates mechanism which in turn shifts the clutch-spool to discontinue the drive to the then operative mechanism and to further shift the clutch-spool to render eiiective the other train. 1 For example, the index mechanism causes the clutch-spool to be shifted to disconnect the index clutch-teeth 56 85 and to engagethe clutch-teeth 56 and Li l of the feed drive train. 0

- rounded outer end to exert a cam action on the .drive to the feed train and to connect the index drive.

l-totatably journaled on the index shaft 96 beuneath the worm-wheel 95 is an arm 102 normally held in contact with a stud 102 carried by the turret clamp cam drum by a coil spring .103 connecting the hub of the lever with said cam drum (see Fig. 14). During the rotation of the index disk 84, the rounded outer end of the arm 102 engages a stud 104 carried by one arm of a two-armed lever 105 fuicrumed at 105 in a bracket 105 secured to the main frame. A detent 119, later to be referred to, temporarily :holds the lever 105 against oscillation whereupon the shaft 96 and cam drum 0 continue to rotate independent of the arm 102, the spring 103 being extended and put under tension. Continued rotation of the cam drum 0 brings a stud 102 into contact with the rear wall of the lever as shown in 14. A further slight rotation of the drum, and pin 102 carried thereby, swings the lever 102 counter-ole .rwise causing its the stud 104, thereby overcoming action of the detent hereinbefore referred to and causing the lever 105 alsoto be swung counter-clockwise The other arm of the lever 105 is connected by alink 106 to an arm 10'? secured upon one end of a shaft 108 journaled in bearings provided by the gear-box. To the other end of the shaft 108 is secured an arm 109 to which is connected one end of a link 110 which, at its other end, is connected to a swinging arm 111 journaled on a stud 112 fixed in the gear-box. A second link 113 connects the arm 111 with one arm 114 of a two armed lever 114 rotatably mounted upon a shaft 115 journaled in the gear-box, which shaft has secured to it a fork 116 engaging the clutch-spool 56.

Fixed upon the outer end of the shaft 115 is an arm 117 having its free end arranged between lugs 114 and 114 projecting from the lever 114. The lever 114 is also formed with a bevelled nose 118 engaging the bevelled end of a spring pressed plunger 119 slidingly mounted in a casing supported by the gear-box. This plunger 119 comprises the detent means which temporarily holds 7 the lever 105 against swinging when the stud 104 thereof is first engaged by the arm 102. As shown in Fig. '7, the lever 114 is in an intermediate position through which it passes in shifting tl e clutch-spool from feed to inder: position vice versa. During thefeeding of the tool heads the plunger 119 engages the upper inclined wall of the nose 118 and during the index of the turret it engages the lower inclined wall thereof. Due to the lost motion between the lugs 114 and 114 and the arm 117 and the action of the spring plunger on the nose 118 of the lever 114, these elements constitute a carry-over mechanism for completing the shifting of the clutch-spool 56. As the rounded outer end of the arm acting on the stud 104, earns the lever 105 counter-clock wise, the lever 114 is rotated clockwise, causing the lower inclined wall of the nose 118 to wipe past the nose of the plunger 119 depressing it in opposition to its spring 119 until the apex of the nose has reached the apex of the plunger, as

, shown in Fig. 7. This initial movement of the lever 114 has no effect upon the arm 11'? or the shaft 115 and fork 116 connected therewith. Instantly upon the passing of the apex of the nose beyond the apex of the plunger, the spring 110 Likewise, rotation of the'feed shaft Q atstation M shiftsthe clutch-spool 56 to discontinue forces outwardly on the plunger and its lower" bevelled edge actsupon the upper bevelled edge of the nose 118, thereby giving the lever 114 quick rotation in a clockwise direction. This movement causes the lug 114 to engage the arm 117 and give it and the shaft 115, and fork 116 connected therewith, a similar clockwise movement thereby shifting the clutch-spool 56 to disengage the index clutch- teeth 56 and 85 and to engage the feed clutch- teeth 56 and 54 The parts are shifted in the opposite directions to disengage the feed drive and to re-engage the index drive by mechanism later to be described. The final clockwise movement of the lever 114, under the influence of the plunger, pulis the links 113 and 1l0'and thereby through arm 109, shaft 108, arm 107, and link 106 causes the lever 105 to be swung clockwise to rnove the stud 104 out of contact with and out of the path of the arm 102. Immediately upon this final movement of the stud, the spring 103 swings the'lever 102 about the shaft 95; bringing the forward wall of lever into contact'with the stop stud 102 The clutch-spool 56, fork lld shaft 115, arm 1'17, and lever 11 4 are swung. counter-clockwise to disengage the feed clutch-teeth and to engage the index clutch-teeth by mechanism. actuated from the feed Q of the station M as now will be escribed. Rotatably mounted on the shaft Q is the hub of an arm 120 which projects outwardly through apertures in the cam drum 38 and in one of the cam sections secured thereto. A spring 120 connected with the hub of the arm and the cam drum 38 norma ly tends to swing the arm clockwise about the shaft but permits it to be moved in the opposite direction. The arm 120 passes through a U-shaped guide 121 secured to the cam drum, which guide prevents movement of the arm axially of the shaft Q. The outer end of the arm carries a earn 120* which, during rotation of the shaft Q, and after the tool slides have been advanced and subsequently substantially retracted, engages a stud 122 carried by an arm 123 fixed upon one end of. a rock shaft V journaled in the gear-box transverse to the axis of the shaft Q. Upon the other end of the shaft V, there is secured anal-m 124 connected by a link 125 with an arm 114 of the lever'114. When, during rota-V tion of the feed shaft Q, the cam 120 engages the stud 122, the arm 120 is temporarily held against rotation with the shaft due to the fact that the arm 123 and parts connected therewith are impositively held against movement by the plunger 119. The arm 120 remains stationary, thereby placing the springl20 under tension until the wal1 121 of the U shaped guide 121 engages the arm and moves it against the resistance offered by the spring-pressed plunger 119. Movement of the arm 120 causes the cam 120 thereof to shift the arm 123 counter-clockwise as viewed in Fig. 12. This movement of the arm 123 effects, through the connection previously described, counter-clockwise movement of the lever 114, shaft 115 and fork 110, thereby shifting the clutch spool 56 to disengage the feed clutch- teeth 56 and 54 and (unless further movement of the fork is prevented by interference means hereinafter to be described) to engage the index clutchteeth 56 and 8.5 to initiate a new cycle. In throwing out the feed, the lever-1'14, arm 117, and plunger 119 act as a carry-over device as hereinbefore described, but in the reverse direction. After the apex of the nose 113 has passed the apex of the plunger and as the lever 114 is moved by the plunger, the arm 123 is swung to the

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