US2159207A - Machine tool - Google Patents

Description

5 Sheets-Sheet l L. E. GODFRIAUX MACHINE TOOL Filed Nov. 13, 1937 May z3, 1939.

ATTORNEY May 23, 1939 l.. E. GoDFRlAux 2,159,207

MACHINE TOO L Filed No?. 13, 1957 5 Sheets-Sheet 2 IINVENTOR i MYwMgM L/a/wm ATTORNEY 23 1939- L. E. GoDFRlAUx 2,159,207

MACHINE TOOL Filed Nov. l5, 1957 5 Sheets-Sheet I5 5w w 31 Si? INVENTOR MM5 n, W6 fm? ATTORNEY L. E. GODFRIAUX MACHINE TOOL Filed Nov. l5, 1957 5 Sheets-Sheet 4 ATTORNEY MalyI 23, 1939.

May 23, 1939- L. E. GODFRIAUX 2,159,207

MACHINE TOOL FiledNOv. 13, 1937 5 Sheets-Sheet 5 Patented May 23, 1939 UNITED STATES PATENT OFFICE MACHINE TOOL Application November 13, 1937, Serial No. 174,358

19 Claims.

This invention relates.to machine tools, and more particularly to lathes of the type generally referred to as chucking lathes.

An object of the invention is generally to simplify and improve the construction and operation of machine tools, and especially of chucking lathes of the type shown in my former Patents No. 1,446,557, dated February 27, 1923, and No.

1,774,917, dated September 2, 1930. Other objects will be apparent to those skilled in the art from the accompanying description.

The invention consists of the construction and arrangement of parts as herein illustrated, described and claimed, and in such modification of the structure illustrated and described as may be equivalent to the structure of the claims.

Throughout the specification the same reference numerals have been applied to the same parts, and in 'the drawings:

Figure 1 is a front elevation of a lathe in which the invention is incorporated..

Figure2 is a sectional elevation taken approximately along line-2 2 of Fig. 1, and enlarged.

Figure 3 is a'plan view, partly in horizontal section taken approximately along line 3-3 of Fig. 2.

Figure 4 is a vertical section, taken approximately along line 4-4 of Fig. 3.

Figure 5 is a rear view of the head end of the lathe, which is the portion at the left in Fig. Il.

Figure 6 is a partial vertical section, taken approximately along line 6 6 of Fig. 4, and enlarged.

Figure 7 is a partial horizontal section, taken approximately along line 'l-l of Fig. 4, and eniarged.

Figure 8 is a partial elevation, viewed from line 8-8 of Fig. 1 and showing certain tool slides.

Figure 9 is a partial section along line 9-9 of Fig. 8.

Figure 10 is a semi-diagrammatic View of a control valve and certain operating mechanism therefor.

Figure 11 is a partial view and section taken 45 along line of Fig. 2.

Referring to the drawings, a base or bed 20, Figs. 1, 4, carries a main spindle 2| rotatably journaied in the left or headstcck end, and a carriage or main slide 22 suitably guided on bed 50 20 for reciprocatory movement parallel with the spindle axis. Spindle 2| carries a work holding chuck 23, and the carriage 22 has ar. end face 24 in the direction of the chuck, upon which are mounted tool slides such as 25, 26, Figs. 1, 8, 9,

` 55` that are suitably guided for substantially radial reciprocatory movement in base portions, such as 25a, 26a, rigidly but removably and interchangeably fixed on end face 24. Tool slides 25, 26 may be provided with suitable tool holders, such as 26h, Fig. 9, for operating on work pieces held in chuck 23. Another tool slide 2l, Fig. 4 is guided for reciprocatory movement parallel with the spindle axis and may carry various tool holders such as the boring tool holder 2lb.

For the rotation of spindle 2| and chuck 23 there isprovided transmission mechanism as follows: A drive pulley 28, Fig. 3, is driven from any suitable power source, such as a motor, not shown, and is fixed on a shaft 26. Rotatably mounted on shaft 29 are spaced gears 30, 3| of different diameter, respectively meshing with the gears 32, 33 fixed on a shaft 34. Associated with the different gears 30, 3| are clutches 35, 36 of any suitable construction, and alternatively operable by the shifting of a clutch spool 3l to drive the one or the other gear 30, 3| from shaft 29, whereby to drive shaft 34 at diifere'nt speeds, except upon operation of certain interrupting mechanism, later described. Shaft 34 is connected to drive a shaft 38 through different diameter gears 39, 4|) which lare removably splined to the ends of shafts 34, 38, and may be reversed in position or replaced by other gear pairs, not shown, for effecting various changes of speed between the shafts. Shaft 38 drives spindle 2| through a pinion 4 Fig. 4, fixed on the shaft and a gear 42 fixed on the spindle. The clutches 35, 36 and the reversibly interchangeable gear pairs such as 39, 40 each provide rate change means for eecting various speeds of spindle 22 while the pulley 28 is driven at constant speed.

For the movement of the carriage 22 and of tool slides 25, 26, 2l there is provided transmission mechanism which includes the spindle transmission previously described and other transmission mechanism as follows: A helical gear 43, Figs. 2, 4, fixed on spindle 2|, drive's a shaft 44 through gear 45. Shaft 44 drives a shaft 46 through a rate changer comprising interchangeable and reversible 'gear pairs such as 41, 48 carried by the shaft ends. A pair'of parallel shafts 49, 50, Figs. 3, 4, are each driven through the rate changer by a gear 5|, Fig. 2, removably xed on the shaft 46 to engage with a gear 52 on shaft 50, an idler 53 engaging gear 52, and a gear 54 removably fixed on shaft 49 and engaging the idler. The gears 52, 54, here shown of the same diameter, may be replaced by other gears having different diameters, whereby to drive shafts 49, at different speeds, the idler riage forward to cutting position by the following mechanism:

A hand lever |2|, Figs. 3, 10, is fixed on a shaft |22, which has fast thereon a lever |23 carrying a. pivoted latch |24. Latch |24 is normally maintained by gravity or by suitable spring means, not shown, in the position shown in Fig. 10, but upon manual movement of the hand lever |2| downwardly the latch |24 moves to the right in Fig. 10 to abut a pin |25 fixed in the hub of cam '||1, whereupon the continued movement of the latch rotates the cam ||1 suiliciently for the cam portion ||1a to move past the complementary contact portion of the levers ||5, ||6 and the levers, together with the valve plungers |09, move down to permit the seatto be manipulated in order to effect a forward movement of the carriage provides a valuable safety feature, particularly when the carriage is operated by compressed air, when the carriage movement is so rapid that if the operator had his hand between the chuck and the cutting tools he might not move quickly enough to avoid injury. The double lever control of the starting valve ||l| requires both the operators hands to be in a position, during the forward movement] where they cannot be injured.

Where the pressure fluid for movement of carriage 22 is air it is desirable to cushion the carriage at the end of the forward and reverse movement. For such purpose there is used a hydraulic cushioning device generally denoted as A, Fig. 1, which includes a piston A| fixed on a piston rod A2 and reciprocable in a body of fluid supplied from a reservoir A3. Piston Al moves between a 'right hand position, shown in Fig. 1, and a similar left hand position. For movement of piston AI the piston rod A2 has exposed abutment ends which are respectively contacted by,

the adjustable abutment screws A4, A5 near the end of the fast reverse and' forward movements. The piston Ai, in this instance, has cone shaped ends, as shown in the drawings, which in the extreme right and left piston positions seat in complementary tapered bores A6, A1. At the start of the piston movement in either direction there is little resistance to the movement Since the fluid within the chambers such as A8, A9' may pass freely out through comparatively large passageway such as A|0, but as the piston approaches its seating position in the tapered bore the area of the passageway is decreased in such manner that the carriage movement is arrested without shock.

The shifter spool 31, Fig. 3, and spool 62, Fig. 4, are primarily for the alternative power engagement respectively of the clutch pairs 35, 36 and 58, 6|, and each of these spools are normally in the one or the other clutch engaging position, as will be later explained, but there is, in addition, manual means for alternatively engaging or disengaging the clutches of either pair, irrespective of which clutch of the pair may be engaged.

For the clutch pair 35, 36 the means for manual engagement or disengagement is as follows: Referring to Figs. 3, 5, a shifter spool |21 is connected for shifting movement with a cam or operating bar |21a, which is housed in a suitable slot in the shaft 29 and extends to provide recesses |21b, |21c respectively for the roller ends of pivoted clutch levers, such as 35a, 36a, of the different clutches. The clutch spool 31 is connected for shifting movement with a cam or operating bar 31a which has wedge or cam shaped opposite ends respectively cooperative with pivoted clutch'levers 35h, 36h. Interposed between the cam bar |21a and the respective ends of the cam bar 31a there are transversely slidable pressure transmitting or equalizing pins 35o, 36e. When the clutch spool 31 is shifted to the left in Fig. 3 the combined dimensions of the cam bar 31a, equalizing pin 35e and cam bar |21b are sufficient to` outwardly pivot the clutch levers 35a, 35h sufficiently to engage the clutch 35, but only if the cam bar |21a has been shifted by shifter spool |21 to a position Where the roller end of the lever 35a does not engage in the recess l21b. Similarly the clutch 36 may be engaged by a right hand movement, Fig. 3 of the shifter spool 31, but only if the shifter spool |21 has been shifted to a position where the roller end of lever 36a does not engage in the recess |210. The recesses |21b, |210 are so spaced as to be simultaneously engaged or disengaged with the roller ends of their respective clutch levers 35a, 36a, and by the described construction it results that in one axial'position of spool |21 the clutches 35, 36 may be respectively engaged in the left and right positions of spool 31, while another axial position of spool |21 neither of the clutches 35, 36 are engaged, whereby the transmission to the spindle 2| and the feed drum 63 is interrupted. Clutch spool |21 may be manually shifted to effect such alternative interruption or engagement of clutches 35, 36 by the means of a hand lever |28, Fig. 2, fixed on shaft |29, Figs. 2, 5, a lever |30, a pivoted connecting rod |3|, a pivoted lever |32 and a member |33 engaging an annular groove |34 in the clutch spool |21.

For the clutch pair 58, 6|, Fig. 4, the means for the manual engagement or disengagement of the clutches is similar to that just described, and therefore will not be described in detail. The manual operating lever for this clutch pair is the lever |35, Figs. 1, 2, which is rotatably supported on shaft |29 and connected for the shifting of a shifter spool |36, Fig. l4, by the means of a pivoted connecting rod |31 and a pivoted lever |38, Figs. 1, 4, the lever |38 having a dependent portion engaging an annular groove in the spool |35. Shifter spools |36 and 62, Fig. 4 are provided with cam or operating bars and associated mechanism, not shown, operatively the same as that previously described for the clutch spools |21, 31 whereby the manual shifting of clutch spool |36 will alternatively interrupt or engage the clutches 58, 6| irrespective of the position of clutch engagement of spool 62.

Control mechanism is provided for the alternative power engagement of the clutch pair 35, 36, Fig. 3, and also of the clutch pair 58, 6|, Fig. 4, at selected points in the rotation of feed drum 63. The mechanism includes a control drum shaft |39, Figs. 1, 4, 5, transversely underlying the shaft 55 and connected to be driven therefrom through the spiral gears |40, IM, the rfi-fio of the gearing being such that one revolution contact portions |45, |46 on a pivoted lever |41 having a dependent arm |48 connected by a pivoted rod |49 to a lever |50 fixed on a shaft Figs. 1, 2. Shaft |5| has a head portion |52 carrying a spring pressed plunger |53, Figs. 2, 11, having an end |53a acting against a cam or detent |54, fixed on a pivoted lever |55 and providing a plurality of point portions |54a, |54b. The lever |55 is connected for movement with another pivoted lever |56, Figs. 2, 11, by the means of an abutment pin |51 and adjustable abutment screws |58, |59, the lever |56 being connected for movement of the clutch spool 62,

. Figs. 2, 4, by apivoted fork member A|60 engag- 4The cam |62 has two sets of spiral grooves, each set consisting of two oppositely angular grooves such as the grooves |68, |69, Fig. 4. When the clutch shifter spool 62 is in the position engaging the clutch 6|, the shifter pin 6| stands in a position slightly separated from cam |62, at the left thereof, as is indicated in Fig. 4, and the plunger |53a, Figs. 2, l1, stands outside the right hand point |54a of the cam |54, as shown in Fig. 11the abutment screws |58, |59 being so adjusted thatat this time there is lost motion between the abutment screw |59 and the pin I 51 as indicated at |10. At this time, also, the detent cam `|54 and plunger |53 have operated to rotate the connecting parts slightly whereby to move the dog abutment portion |46, Fig. 1, upwardly from the position there shown into the path of one of the dogs |43, |44. If the machine operation requires the shifting of clutch .spool 62, Fig. 4 to engage clutch 58 instead of clutch 6|, one of the dogs is used to shift the upwardly displaced dog abutment portion |46 downward whereby to rotate shaft 5| suiilcie'ntly for the point of the plunger |53 to move to the other side of the cam point |54b and the lost motion then permits the cam |54 to quickly shift the lever |55 sufdciently for the pin |6| to enter one of the spiral grooves |68, |69 in the shifter cam |62. The shifter cam then continues the movement of lever |55 to disengage the clutch 6| and to engage the clutch 58, at which time the various parts will be then vpositioned for a similar power shifting in Ythe other direction to be initiated at any desired time in the machine cycle by the other dog |43, |44, operating on the other dog abutment |45 to again disengage clutch 58 and engage clutch 6|. By the means of dogs such as |43, |44, suitably positioned, clutches 58, 6| can be alternatively-engaged at any point in the cycle of operation of feed drum 63.

The mechanism for alternative power engagement of the clutches 35, 36 at any time in` the machine cycle is similar to that just described,

there being for this purpose another dog drum |1|, Fig. 5, fixed at the rear end of shaft |39 and operative through a lever |12, rod |13, lever |14 and shaft |16 to shift a detent plunger |16, Fig.

- 2, whereby to cause engagement of a shifter pin |11 with oneof the cam grooves in the shifter cam |62, the pin |11being carried on a lever |18 havinga hub |18a upon which is xed a lever |19 having a lost motion connection at |80 with a clutch lever |8| carrying a pivoted shifter fork |82 engagingl a suitable annular groove in theclutch'shifter spool 31, Figs. 2, 3.

'I'he power shifter mechanism described for the shifting of the clutch pair 58, 6| is also utilized for the shifting of the clutch spool |21 to disengage the clutch pair 35, 36 whereby to stop rotation of spindle 2| and of the feed drum 63 upon completion ofthe operating cycle, that is to say at the completion of each revolution of the feed drum 63. The mechanism is as follows: A collar |85, Figs. 2, 11, is fixed on the shaft |29, which is connected for shifting the shifter spool |21 by the mechanism previously described.

Collar |85 has a portion cut away to provide an abutment |86 which may be engaged by an abutment |81 on a pivoted latch or dog |88 carried on a pivot pin |89 which is fixed in the lever |55. Latch |88 is normally urged by a spring |90 to a position where abutments |86, |81 will engage and rotate shaft |29, whereby to shift clutch spool 21 to disengage the clutch pair 35, 36, during any clockwise rotation, Fig. 11, of the lever |55, such as is effected by the power shifter cam |62,'Fig. 4, as previously described, during the dog controlled shifting of clutch spool 62 to a position to engage the clutch 6|. The dogs on the control drum |42, Fig. 1, are set to eiect the disengagement of clutches 35, 3,6, as just described, whereby to interrupt the spindle and drum transmission, at substantially the same time that the cam ||1, Fig. 10, has rotated t0 the position Where valve |0| is operative to return the carriage 22 to the loading position, as previously described, thereby completing the operating cycle of the machine.

It is desirable that, after the disengagement of clutch pair 35, 36, as just described, the abutment |86, Fig. 11 should be disengaged-trom the abutment |81, whereby the clutch pair 35, 36 may be again engaged by the reverse movement of shaft |29 without disturbingthe engagement of clutch 6| as, for instance, for starting a new machine cycle, as later described, or during the setting up of the machine. To effect such disengagement of the abutments there is provided a pin |9|, Figs. 2, 11, which is xed with bed 20 to engage the latch |89 and turn it'to the abutment disengaging position shown in Fig. 11.

'Ihe fast forward movement of carriage 22 to cutting position at the beginning of each operating cycle, as previously described, also shifts the spool |21 to the' position engaging one or the other of cluthes 35, 36, according to which of these clutches was engaged at the end of the preceding cycle. For this purpose there is provided a dog |92, Fig. 5, adjustably fixed on carriage 22 and adapted, during forward movement of the carriage, to shift a pivoted lever |93, and thereby shift spool 21 through a pivoted rod |94, an abutment |95 and an abutment pin |96 fixed in the lever |30, which is connected to the spool |21 through the mechanism previously de scribed. It is necessary to subsequently disengage abutment, |95-from pin |96 in order vthat the spool |21 can be shifted, as previously de scribed, for clutch disengagement at the end of the operating cycle. For such disengagement there is provided a cam member |91, Fig. 5, rotatable with the dog drum |1| and adapted to lift the rod |94 sufficiently for such disengagement. If desired the cam |91 may be formed to disengage the abutment |95 immediately following the start of the operating cycle and to maintain such disengagement throughout the cycle, whereby the clutch spool |21 may be manually shifted by the hand lever |28 to interrupt the cycle at any point. A dog |98 adjustably xed on carriage 22, shifts the lever |93 in the reverse direction during the return of the carriage to loading position to insure that the rod |94 is positioned to effect an operative position of the abutment |95 and pin |96 at the next forward movement of the carriage.

In the operation of the machine, assuming that the feed drum 63 is in the position shown in Fig. 4, and thecarriage 22 is in its rear orloading position, which are the positions of these parts at vthe end of a cycle of machine movement, a new cycle is started by manually moving both the levers |2|, |26, Fig. 3, downwardly, thereby admitting pressure fluid through valve to quickly move the carriage 22 forward to working position, as previously described. During such movement the carriage dog |92 engages one of the clutches 35 or 36 and` starts the rotation of the spindle 2| and of feed drum 63, and feed cam slot 12 then assumes control of the position of the carriage, giving to it such forward or reverse movement or dwell as may be necessary to the work piece being machined. During the feed drum rotation the cam grooves 86, 88, 9| similarly control the movement of tool slides 25, 26, 21. The time required for the rotation of the feed drum is determined by the setting of the various rate changers n the spindle and feed drum trains, but in any setting of the rate changers the clutch control drums 42, |1| will make one revolution during one revolution of the feed drum 63. At the completion of the rotation of feed drum 63 the control cam ||1 for valve ||l| operates the valve to quickly move the carriage back to loading position, and at the same time one of the dogs |43, |44 on dog drum |42 op erates to disengage the clutches 35, 36 to stop the rotation of the spindle and feed drum. This completes the operating cycle of the machine.

What is-claimed is:

1. In a lathe having a carriage reciprocable between loading and cutting positions and a reciprocable cross slide member carried thereon, the combination of a rotatable cam drum connected for movement of said cross slide member, a transmission for rotation of said drum, a power train for said carriage movement, manually operable control means for connection of said power train to effect carriage movement to said cutting position and substantially simultaneously to connect said drum transmission, and control means subsequently'operative at a predetermined point in the rotation of said drum to connect said carriagetrain to effect carriage movement to said loading position and substantially simultaneously to disconect said drum transmission.

2. In a lathe having a carriage reciprocable between loading and cutting positions and a reciprocable cross slide member carried thereon, the combination of ay rotatable camy drum connected for movement of said cross slide member, a transmission for rotation of said drum, a power train for said carriage movement, manually operable control means for conection of said power train to effect carriage movement to said cutting position and substantially simultaneously to connect said drum transmission, control means sub sequently operative at a predetermined point in the rotation of said drum to connect said carriage train to eii'ect carriage movement to said loading position and substantially simultaneously to disconnect said drum transmission, said manually operable control means including two spaced hand levers requiring simultaneous displacement for the connection of the power train.

3. In a lathe having a rotatable work spindle, a carriage reciprocable between loading and cutting positions, and a tool slide member reciprocable on said carriage, the combination of a rotatable cam drum connected for reciprocation of said slide member, a transmission for rotation of said spindle and drum including a clutch having engaged and disengaged positions, a power train for said carriage movement, manually operable control means for connection of said power train to effect carriage movement to said cutting position and to substantially simultaneously shift said clutch to engaged position, and control means subsequently operative at a predetermined point in the rotation of said drum to connect said power train to effect carriage movement to said loading position and to substantially simultaneously shift said clutch to disengaged position.

4. In a lathe having a rotatable work spindle, a carriage reciprocable between loading and cutting positions, and a tool slide member reciprocable on said carriage, the combination of a rotatable cam drum connected for reciprocation of said slide member, a transmission for rotation of said spindle and drum including a clutch having engaged and disengaged positions, a power train for said carriage movement, manually operable control means for connection of said power train to effect carriage movement to said cutting position and to substantially simultaneously shift said clutch to engaged position, and control means subsequently operative at a predetermined point in the rotation of said drum to connect said power train to effect carriage movement to said loading position and to substantially simultaneously shift said clutch to disengaged position, said manually operable control means including two spaced hand levers and connections requiring simultaneous displacement of said levers for the connection of the power train.

5. In a lathe having a rotatable spindle the combination of a carriage reciprocable in a path parallel to the spindle axis and having an end face in the direction of said spindle and transverse to the spindle axis, a cross slide unit removably fixed on said end face and including a reciprocable cross slide member and a driving member therefor, a complementary driving member on said carriage, said driving members being adapted for driving engagement during replacement of said unit following removal thereof, and transmission mechanism for rotation of said spindle and actuation of said complementary driving member.

6. In a lathe having a rotatable spindle the combination of a carriage reciprocable in a path parallel to the spindle axis and having an end face in the direction of said spindle and transverse to the spindle axis, a cross slide unit removably fixed on said end face and including a reciprocable cross slide member and a driving member therefor, a complementary driving member on said carriage, said driving members being adapted for driving engagement-during. replacement of said unit following removal thereon, and transmission mechanism for rotation of said spindle and actuation of, said complementary driving member, said transmission including cam means carried by said carriage for bodily reciprocation therewith.

7. In a machine tool having a movable support, the combination of transmission mechanism for movement of said support at a feed rate, power means for relatively fast movement of said support, and fluid cushioning means operative only for said relatively fast movement including a cylinder, a piston relatively reciprocable therein, and means altering the resistance to displacement of fluid in -said cylinder in accordance with a change in the relative position of said cylinder and piston.

8. In a machine tool having a movable support, the combination of transmission mechanism for movement of said support at a feed rate, power means for relatively fast movement of said. support in either of opposite directions between spaced positions, and fluid cushioning means op-A erative only for said relatively fast. movement including piston and cylinder means operative in each of said directions to cushion the support upon approach thereof to the spaced position for the corresponding direction.

9. In a machine tool having a base, a rotatable spindle and a reciprocable support, the combination of a rotatable feed cam drum, a transmission. including main clutch means in serial driving relation withboth said spindle and feed drum and shiftable to engaged and motion interrupting positions, a power train for relatively fast movement of said support in either direction` exclusive of said clutch means, and shifter mechanism operable upon support movement from said power train for shifting said clutch means from one to the other of said positions.

10. In a lathe having a base, a rotatable work spindle and a reclprocable tool carriage, the combination of a rotatable feed cam drum,la transmission for rotation of said spindle and cam drum including a clutch shiftable to engaged and motion interrupting positions, a slide reciprocably carried by said carriage, a power train for movement of said slide including cam means rotatable with said feed drum, a power train for relatively fast movement of said carriage exclusive of said clutch, and shifter mechanism operable upon carriage movement from ,said power train for shifting said clutch from the one to the other of said positions.

11. In a lathe having a rotatable work spindle and a reciprocable tool carriage, the combination of a feed cam drum rotatably supported on said carriage, a transmission including main clutch means in serial driving relation with both said spindle and drum and shiftable to engaged and motion interrupting positions, a power train for relatively fast movement of said carriage exclusive of said clutch means, andshifter mechanism operable upon carriage movement from said power train for shifting said clutch means from the one to the other of said positions.-

12. In a machine tool providing a tool support and a work support relatively reciprocable between loading and operating positions, the combination of a feed rate train for said relative support movement, a power train for relatively fast relative movement of said supports from said loading to operating position.' and'control means v for connecting said power train including two hand levers, said control means requiring simultaneous displacement of said levers to connect said train.w Y Y 13. In a lathe the combination `of a bed. a carriage reciprocably carried by said bed' and providing an end face in a plane transverse to the path of said reciprocatory movement, a

' plurality of cross slide units removably fixed on said end face and each providing a cross slide member reciprocable in a path transverse to the path of carriage movement, a rotatable cam drum axially parallel to the path of carriage movement, a plurality of cams on said drum and respectively connected for movement of different of said cross slide members, power means for rotation of said drum, and means for interruption of said power means at a predetermined point in the drum rotation. v

14. In a lathe the combination of a bed, a carriage reciprocably lcarried by said bed and providing an end face in a plane transverse to the path of said reciprocatory movement, a cross slide unit removably xed on said end face and providing va cross slide member reciprocable in a path transverse tothe path of carriage movement, a rotatable cam drum axially parallel to` the path of carriage movement, a cam on said' drum and connected for movement of said cross slide member, a transmission for rotation of said drum, a power train for movement of said carriage between loading and operating.

positions, means for interruption of said transmission at a predetermined point in the rotation of said drum, and means for subsequently reconnecting said transmission. during' carriage movement between said positions.

l5. In a lathe the combination of al bed, a carriage reciprocably carried by said bed and providing an end face '1n a plarie transverse to the path of said r'eciprocatory movement, a cross slide unit removably fixed on said end face and providing a cross slide member reciprocable in a path transverse to the path of carriage movement, a rotatablecam drum axially parallel to the path of carriage movement, a cam on said drum and connected for movement of said c'ross slide member, a transmission for rotation of said drum, a power train for relatively fast movement of said carriage between loading and operating positions, manually operable control the combination of a carriage reciprocable in a path parallel with the spindle axis, a slide member movable on said carriage in a path transverse to said axis, a cam drum rotatably mounted on said carriage, a plurality of cams on said drum and respectively connected for carriage movement in said parallel path and for member movement in said transverse path, transmission Amechanism for rotation 4of said spindle and of said drum, and other'transmission mechanism for relatively fast movement of said carriage in said path between spaced loading and cutting positions.

17. In a lathe having a rotatable work spindle the combination ot a carriage reciprocabie in a path parallel with the spindle axis, a slide member movable on said carriage in a path transverse to said axis, a cam drum rotatably mounted on said carriage, a plurality of cams on said drum and respectively coonnected for carriage movement in said parallel path and for member movement in said transverse path, transmission mechanism for rotation of said spindle and of said drum, other transmission mechanism for relatively fast movement of said carriage in said path between spaced loading and cutting positions, and control mechanism for the control of each transmission in accordance with movement derived from the otherv transmission.

- 18. In a lathe having a rotatable work spindle the combination of a tool carriage reciprocable in a path parallelto the axis oi' said spindie.saidcarx'ialzehavinganendfaceintheA direction of said spindle and in a plane substantially perpendicular to said aiis, a tool carrier unit removably nxed on said end face and includina` a tool slide member reciprocable in a pathsubstantially parallel to said plane, and power means for movement of said carriage and tool carrier inciuding a tool carrier tion portion bodily reciprocable with said carriage.

19. In a machine tool having a carriage reciprocable between loading and cutting'positions, the combination of a feed rate transmission for said carriage, power means for relatively very fast movement o! said carriage from said loading to said cutting position, and control means !orconnection of said power means including ltwo spaced hand levers requiring simultaneous displacement to eect said connection, the spacing of said hand levers beingsufilcient to require operation or the levers respectively by different hands of an operator.

LOUIS EDWARD GODFRIAUX.

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