US2360118A - Work support - Google Patents

Description

WORK SUPPORT Filed NOV. 23, 1942 13 Sheets-Sheet l v I ma Hunfizverziors E'Gallimore Evere/ ft? fi o/we s,

d- 1944- K. F. GALLIMORE ETAL 0 1 WORK SUPPORT Filed Nov. 23, 1942 l3 Sheets- Sheet 3 Oct. 10, 1944. K. F. GALLIMORE ET AL 2,360,113

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Oct. 10, 1944.

K. F. GALLIMORE ET AL WORK SUPPORT Filed Nov. 23, 1942' 13 Sheets-Sheet 7 7- allimore [Och K. F. GALLIMQRE ETAL 2,360,113

WORK SUPPORT fj'gm.

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Filed Nov. 23, 1942 K. 'F. GALLIMORE ET AL WORK SUPPORT 13 Sheets-Sheet 9 054. flight-444M Oct. 10, 1944.

K.F. GALLIMORE ET AL WORKSUPPORT Filed NOV. 23, 1942 l3 Sheets-Sheet 10 5 T m ,w T

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I K. F. GALLIMORE ET AL 2,360,118

WORK SUPPORT Filed NOV. 25, 1942 13 Sheets-Sheet ll TTOQN mys 0 1944- K. F. GALLIMORE ET AL 2,360,118

WORK SUPPORT Filed NOV. 23, 1942 13 Sheets-Sheet l2 s @W i w MW; TM. M 2% VG mi eV Q5 a 10, '1944- K. F. GALLIMORE ETAL 2,330,118

1 WORK SUPPORT Filed Nov. 23, 1942 1a sheet-sneet 1s EN v E. N TOQ$ patented Get. l0, i944 WORK sprroar Keith 1F. Gallimore and Everett K. Morgan, Fond du lac, Wia, assignors to Giddings 8.. Lewis Machine Tool 30., Fond du Lac, Wia, a corporation of Wisconsin Application November 23, 1942, Serial No. 466,558

25 Claims.

The invention relates to an improved work support for heavy. duty machine tools, particularly suitable for use with horizontal boring,

drilling and milling machines.

One object of the invention is to provide a work supportof the above general character, embodying in a single unitary structure, a table or the like operative to hold a large heavy workpiece in position to be operated on by the tool together with power means operable selectively to translate the entire supporting structure and the work toward or from the tool or to rotate the table and work about a horizontal axis at either a rapid traverse rate or at a slower variable feed rate.

Another object is to provide an improved rotary work support adapted for use with horizontal boring, drilling and milling machines of either the table type or floor type.

Another object is to provide novel means for supporting the peripheral edge of a rotatable work table to efiectually prevent the deflection of the table under load.

Still another object is to provide clamping means of novel and improved construction adapted for use with rotatable or translatable machine elements and operative to positively clamp the movable elements to the machine frame. 1

A further object resides in the construction and arrangement of the frame work, table, driving mechanism and other elements of the work supporting structure to adapt it for use with extremely large workpieces andfor what is commonly known as heavy duty service.

()ther objects and advantages of the invention will become apparent from the following detailed description of the preferred embodiment illustrated in the accompanying drawings, in which:

- Figure 1 is aside elevational view of a work support embodying the features of the invention.

Fig. 2 is a front elevational view of the'work support.

, Fig. 3 is a plan view of the work support.

Fig. 4 is a fragmentary sectional view taken in a horizontal. plane through the axis of the table supporting spindle substantially along the line of l---- l of Fig. 2. I

Fig. 5 is a, vertical sectional'view taken 'along the line 5-5of Fig. 2.

Fig. 6 a diagrammatic view of thedrive mechanism.

Fig. '7 is a. horizontal sectional view taken along the line ll of Fig. 2 showing the drive mechanism in plan.

Fig. 81s a diagrammatic view of the hydraulic control and lubricating systems.

Fig. 9 is a sectional view of the clamping mechanism taken along the line Q@ of Fig. 10

with parts broken away to show details of construction.

Fig. 10 is a plan view of the clamping mechanism taken in a horizontal plane substantially device taken in a plane substantially on the line Fig. 14 is a vertical sectional view of the feed and rapid traverse selector unit taken, on the line M-H3 of Fig. 7.

Fig. 15 is a plan view of the feed selector unit.

Fig. 16 is a longitudinal vertical sectional view of the feed selector unit taken along the line Ill-l6 of Fig. 7. v

Fig. 17 is a vertical sectional view of the saddle driving mechanism taken along the line il--l1 I of Fig. 16

Fig. 18 is an 'end view of the table feed reduction mechanism taken in a vertical plane substantially on the line ill-l 8 of Fig. '7.

Fig. 19 is a vertical sectional view taken along the line l9-l9 of Fig. 18.

Fig. 20 is a. developedv sectional view of the hand feed mechanism for the rotary table.

Fig. 21 is a fragmentary vertical sectional vie taken along the line 2l--2l of Fig. 1.

While the invention is susceptible of various modifications and alternative constructions, we

have shown in the drawings and will herein-de-.

scribe in detail the preferred embodiment, but

it is to be understood that we do not thereby intendto limit the invention to the. specific form disclosed, but intend to cover all modifications,

adaptations andalternative constructions falling within the spirit. and scope of the invention as I defined in the appended claims.

' For purposes ofexernplification, the improved work support comprising the present invention has been shown in the form most sultable for use with heavy duty horizontal bo in drilling and milling machines; Referring to Figs. 1, 2 and 3 of the drawings, the work support, as herein shown, comprises a carriage or saddle 30 adapted to b slidably supported on horizontal ways 3| formed on the upper face of an elongated base or bed 32. The bed may be a part of an existing table type horizontal boring, drilling and milling machine or it may be supplied especially for the work support if desired. The bed, as shown, is

of box type construction and is provided with three of the ways 3|. Bolted orotherwise rigidly secured to the bed, inside the two outer ways, are a pair of inwardly facing racks 33, utilized in traversing the saddle on the ways, as will appear presently.

Rising from the saddle 30 is a column-like structure including a sub-base 35, a base 36' and casting generally rectangular in horizontal section and having its lower surface machined to form bearings for engagement with the ways 3|. The saddle is held securely on the ways by looking plates 43 carriedv on flanges 4| depending from opposite side edges of the saddle. Parallel depending ribs 42 On the underside of the saddle cooperate with vertical guide surfaces formed on opposite sides of the center way to guide the saddle in its reciprocation on the ways. Suitable gib plates 42 may be provided as required for adjusting purposes.

As will be seen by reference to Figs. 5 and l of the drawings, the subbase 35 is in the form of the frame section and is spaced rearwardly from the front bearing so as to hold the spindle rigidly against lateral movement.

The bearings 53 and 54 are arranged in opposed relation and the latter is provided with adJusting mechanism by which both bearings may be preloaded. This mechanism may be of any suitable and well-known type and as herein shown comprises a ring 55 encircling the spindle and having a plurality of screw-threaded members 51 projecting from one side to engage the inner race ring of the bearing 54. Movement of the ring 56 rearwardly of the spindle is blocked by a removable abutment in the form of a split ring 58 engaging in'a peripheral groove in the spindle. The spindlev and bearings may thus-be forced into tight preloaded engagement by screwing in the threaded members 51.

The rear bearing 55 provides additional support for the spindle at the end remote from the table. As herein shown, this bearing is ofthe opposed roller type and is provided with adjusting mechanism 59 similar to that above described. The bearing is supported in a bracket 80 bolted to the top of the base 38. A housing 5| encloses the bearing bracket and the end of the spindle projecting beyond the intermediate bearing 54.

The table is preferably in the form of a heavily ribbed casting, circular in contour, and recessed centrally for the reception of the spindle pilot 5|. Inset from the periphery of the table is an integraL; rearwardly-.projecting flange 52 to which is bolted or otherwise rigidly secured an annular worm wheel 55 adapted to be driven by a cone-type worm 54 (Figs. 4 and 6) fast on v a vertical shaft 55 extending upwardly from a box-like casting generally rectangular in hcrizontal section and having an outwardly projecting flange 44 by which it may be bolted to the saddle 30. The sub-base is provided with internal ribs or webs 45 to make it sturdy and rigid, such ribs being suitably arranged to provide space for the reception of the various units of the drive mechanism to be described hereinafter. Openings in the side walis of the sub-base provide convenient access to the drive units, such openings being provided with sheet metal covers 45.

The base 38 (Fig. 5) is likewise a heavily ribbed, box-like rectangular casting and is provided at its lower edge with a flange for bolting it to the sub-base". The frame 31 rises from the front edge of the base and comprises a central section 41 (Fig. 5) having spaced bearing seats 48 and 49 for supporting the table spindle 39. A

base of the pilot for bolting the table to the "spindle. The spindle is mounted for rotation in large tapered roller bearings, three such bearings 53, '54 and 55 being provided in the present-in- "stance. The bearing 53-18 mounted-in the front bearing seat "of the frame section 41 as close to the table as practicable. The intermediate bearing54ismountedintherearbearin seat 48 of spindle. An integral flange 52 is provided atthe the sub-base 35 as shown in Fig. 2. Intermediate the periphery of the table and the flange 82 is-mounted a hardened steel ring 66 (Figs. 4, 5, 9 and 11-13) formedwith outwardly facing teeth 51. adapted to cooperate with clamping means to be described hereinafter. The face of the table is formed with transverse parallel T- 7 slots 58 for securing the work to the table.

Means is provided for positively clamping the table 41! to the machine frame to hold it securely in fixed position while a tool is operating on a workpiece. This means, as herein shown, comprises a clamping plate 10 (Figs. 5, 9 and 10) having one side edge formed with relatively flne rack teeth 1| adapted to mesh with the teeth 51 of the locking ring 56 secured to the table. The clamping plate is slidably supported and guided in a housing comprising a bottom plate 12 having upstanding flanges 13 along each side edge to which a cover plate 14 is suitably secured. The housing is rigidly anchored tothe base 36 with the locking plate in position for cooperation with the teeth of the ring 65.

The clamping plate is yieldably urged outwardly from the housing, that is, toward the locking ring in any suitable manner. As herein shown, the means provided for this purpose comprises a pair of cylindrical plungers 15 seated in recesses in a pad 15 upstanding from the bottom plate of the housing. Each plunger is provided at its outer end 'with a roller 11 engageable with the rear edge of the clamping plate and coiled compression springs 18 acting on the inner ends of the plungers serve to force the rollers against the plate. A spring pressed plunger 15 located between the two plate shifting plungers plate to maintain it in centered position with respect to the first mentioned plungers.

The clamping plate is shifted to and held in a withdrawn position against the action of the plungers 15 by an eccentric or cam 80 integral with a rock shaft 8| journaled in the bottom and cover plates of the housing and extending through an aperture in the locking plate. The cam coacts with a forwardly facing surface 82 defined by the aperture to retract the locking plate when the shaft 8| is rocked into the position shown in Fig. 9. As the shaft is rocked out of that position, the cam is withdrawn from the surface 82, thus permitting the clamping plate to shift forwardly under the influence of the plungers i and thereby engage the rack teeth H with the teeth of the ring 66.

Means is providedfor accurately centering the clamping plate in its advanced-or operated position and for positively clamping it in a position to preclude any rotative movement of the work table. This means, as herein shown, comprises a pair of wedge members 83 slidably supported in the housing with the clamping plateand on opposite sides thereof for cooperation with the side edges of the plate which are tapered grad-,

ually from front to rear as shown in Fig. 9. The wedge members are guided for movement toward and from the ring 66 by ribs 84 (Fig. engaging in complementary grooves 85 in the bottom plate F2. The arrangement is such that the wedge members upon moving forwardly engage opposite side edges of the clamping plate and positively hold it in forward or operated position to which it was initially shifted by the plungers i5.

The operation of the wedge members is coordinated with the release and retraction of the clamping plate ,by the cam 80 by utilizing this cam for shifting the wedge members. To this end the cam is seated in a closely fitting recess in a cross member or link 86 arranged to extend over the outer faces of the clamping plate and the wedge membersas shown in Figs. 9 and 10. The cover plate 14 serves to maintain the link in position in the housing. Pins 87 projecting from the inner side of the link engage in transverse slots 88 in the respective wedge members to provide an operative connection between the link and the members. Due to this pin-and-slot.

connection, the link is free to move in an arcuate path defined by the cam 80 in response to rocking of the cam shaft. The forward and rearward increments'of such movements are imparted to the wedge members to shift them into or-out of clamping position.

While any sultablemeans may be utilized t Clamping mechanism similar in all respects to that above described, is also provided on the saddie for positively clamping that machine part in fixed position on the ways. In this instance the locking plate 10 is positioned to engage a rack 95 fixed to the side wall of the machine bed .32 as shown in Figs. 1 and 2. The elements of the saddle clamping mechanism are identified by the same reference characters as the corresponding elements of the table clamping mechanism with the additions of the suffix a.

Novel means is provided for supporting the work table adjacent its periphery to counteract any tendency for the table to deflect under load. As the tool is ordinarily applied to the work at a point below the axis of the table spindle, the

supporting means is associated with the lower portion of the table. This supporting means, as

shown in Figs. 1, 2 and 11 to 13, comprises a plurality of adjustable supporting devices I00 mounted on the machine base 36 and arranged to bear against a suitable track carried on the inner side of the table. The track, in this instance, is formed by the outer surface of the hardened ring 86 previously described. As the supporting devices are alike in construction, a description of one will be sufficient.

Referring now to Figs. 11-13, the supporting device H10, in its preferred form, comprises a.

block or shoe i0! of bronze or other suitable material having a flat bearing surface I 02 adapted to engage the face'of the ring 66. The shoe is supported by needle bearings on an eccentric I03 formed on a shaft I04 which in turn is sup ported at opposite sides of the eccentric in needle bearings Hi5 and W6 carriedby a bracket i0! secured to the machine base. a

Splined to the forward end of the shaft MN is a crank arm I08 having its tip p rtion bifurcated to straddle a bolt I09. A nut H0 threaded on the end of the bolt is formed with a convex surface adapted to engage a complementary con-'- cave surface on the crank arm. The bolt I09 is disposed transversely of the shaft 806 and is slidably supported in an aperture in a lug HI projecting laterally from one side of the bracket I01. A coiled compression spring interposed be:- tween the lug and a cup-shaped cap member H3 abutting the head of the bolt urges it outwardly orto the right as viewed in Figs. 11 and 13-. Through the connection provided by the nut H0 and crank arm I 08, the shaft I04 is thus rocked in a direction to force the shoe llll against the rock the cam shaft 8| forclamping'and releasing the table, it is desirable to employ power actuated means, preferablypressure fluid operated, for this purpose because of the severe strains to which the table is subjected in heavy duty service. Theactuating means, as herein shown, com= prises a piston 90 (Figs. 8-10) working in a cylinder 9| bolted or otherwise secured to one side of the clamping plate housing. The piston is dilated with a rod" 92 extending transversely across the housing at one side of the cam shaft.

Rack teeth 93 formed on the piston rod engage the teeth of the pinion 94 fast on the cam shaft.

.. With this arrangement positive locking of the table isobtained by the wedging action of the members 83 o'nthe plate 10 which effectually prevents disengagement of the plate by reason of the strains imposed on the table.

rear face of the ring 66. The pressure exerted by the shoe on the ring may be regulated as required for any particular'work bysimply turning the bolt in the nut I It] so as to vary the 'tenslon of the spring H2. Y

The general form and arrangement of the novel drive mechanism provided by the invention may be readily seen by reference to Fig. 6 of the drawings in which the relationship between the various elements is shown diagrammatically. It-

may be noted, at this time, that the drive mechanism is built up of a plurality of separate structural units which materially simplifies manufacture and initial assembly of the machine and which greatly facilitates removal .of the parts for repair or replacement.

Due to the weight of the parts-to be moved in a work supporting structure of the type under construction. it has been found desirable to utilize separate electric motors M'and M (Figs. 6

and '7) for effecting such movements at rapid traverse and slow feed rates respectively. The

motor M may be of the reversible type to adapt it for driving the parts in either direction. Motor M may be of the unidirectional type with reversal of the drive effected through a-suitable transmission. A feed and rapid traverse selector unit A is provided for connecting these motors selectively with a main drive shaft I20. In the exemplary machine, a heavy duty multiple disc clutch I2I (see also Fig. 14) is provided for connecting up the rapid traverse motor while a positively acting clutch I22 performs this function for the slow feed. The clutches are adapted to be engaged selectively or to be set-to neutral position by remote control through the medium; of pressure fluid operated clutch actuating mechanism shown in Figs. 8 and 14 of the drawings and described hereinafter.

As the rapid traverse drive is used primarily for making rough positioning adjustments of the work, a single traverse rate is satisfactory. The slow feed drive, however, is employed for fine adjustment where a high degree of accuracy is required, and it is therefore desirable to provide for varying the slow feed rate over a relatively wide range. The slow feed drive is, therefore, taken through a, variable speed hydraulic transmission H which is driven from the motor M, in this instance, by a multiple V-belt drive I23. The transmission H may be of any suitable and well known typ a d is desirably provided with a reversing and speed regulating motor RM so that the necessary adjustments may be effected by remote control.

Means is also provided whereby the main drive shaft I20 may be coupled selectively with, suit-, able driving mechanism for'rotating the table 40 or for driving the saddle 30 along the machine bed. To this end the drive shaft I20'isarranged to drive an intermediate shaft I24 forming a part of a feed selector unit B. This drive is effected through a worm I25 on the main shaft and a worm wheel I26 on the intermediate shaft.

The selector unit includes a, pair of mechanically interconnected clutches I21 and I28 (see also Figs. 15 and 16)v operable to connect the shaft I24 with either of two axially alined shafts I29 and I30. The clutches are adapted to be shifted to their respective engaged positions orto a neutral position by a fluid actuator shown in Figs. 8 and 15 and described hereinafter., The

' shaft I29 through bevel gears I3I and I32 drives a horizontal shaft I33 leading to a speed reducing unit (Figs. 6, 7, 18 and 19) which, in turn, drives the vertical shaft 65 carrying the table driving worm 64. The shaft I30 is drivingly connected through gears I34'and I35 (Figs. 6 and 16) with a saddle drive shaft I36 having removably coupled sections I31 and I38 drivingly coupled with vertical shafts I39 (Figs. 6 and 17) disposed at opposite sides of the saddle. The vertical shafts carry pinions I40 meshing with the racks 33 on the machine bed. The drive for each vertical shaft 138 includes a worm I4I fast on the associated shaft sections I31 and I38 cooperating with a worm wheel I42 fast on the pinion shaft.

In additionto the power drive means above described, auxiliary drive units D and E are profast on a shaft I5I which carries a suitable indicator' or dial I52 for indicating the degree of movement imparted to the table. A clutchgear I53 fixed on an axially slidable shaft I54 is adapted to be shifted into or out of mesh with the gear I49. The shaft I54 is turned by a hand crank I55 having clutch teeth engaging complementary teeth I56 at one end of a sleeve member I51 fixed to the shaft and projecting at one side of the saddle. A spring I58 acting on the sleeve I51 yielda-bly urges the shaft and gear I53 to the disengaged position shown in Fig. 20 but permits engagement of the gear I53 with gear I when the table is to be-driven manually. The various gear shafts above mentioned are journaled in a housing I58 adapted to be secured to the side of the sub-base 35.

The hand drive unit E for the saddle is similar to the unit D except that it has a smaller speed reduction ratio. As shown diagrammatically'in Fig. 6, a shaft I60 (see also Figs. 15 and 16) coupled with'the shaft I30 extends to the unit and is provided with a gear I6I meshing with a pinion I62 on a shaft I63. Also fast on the shaft I63 is a gear I64 and an indicator or dial 65 adapted toindicate the degree of movement imparted to the saddle. A clutch gear I66 fast on an axially slidable shaft I61 is adapted to be moved into or out of mesh with the gear I64. Shaft I61 is turned by a hand crank I68 through a clutch connection similar to that above described.

It will be apparent from the foregoing that the entire work supporting structure may be traversed alongthe machine bed at either a rapid traverse rate or at a selected slow feed rate as desired by suitable manipulation of the clutches I2I, I22 and I28. Alternatively, the table 40 may be rotated at a rapid traverse rate or at a selected slow feed rate by appropriate manipulacomprises a generally rectangular housing I60 I:

. stitutes the driven member of the clutch I2I.

tion of the clutches I 2|, I22 and I21. Moreover, these movable machine parts may be driven manually independently of the power drive mechanism when desired.

Reference may now be had to Figs. 14-20 of the drawings for a more detailed disclosure of the power drive mechanism. Thus, as shown in Fig. 14, the rapid traverse and feed selector unit A adapted to be rigidly secured to the top of the the housing on spaced anti-friction bearings is a short shaft I6I having on its outer end a coupling member I62 adapted to cooperate with a companion member I63 on the shaft I64 of the rapid traverse motor M. The other end of the shaft I6I is formed with an enlarged cup-shaped head I65 which constitutes the driving member of the clutch I2 I.

Alined axially with the shaft I6I is a sectional shaft I66. One end of the latter shaft is supported in a bearing I61 seated in a counter bore in the adjacent end of the shaft I6I. The opposite end of the shaft I66 projects through the side wall of the housing I60 and is provided with a coupling member adapted to cooperate with a companion member I68 (Fig. 15) on the main drive shaft I20. A bearing I61 carried on the housing I60 supports the shaft I66 adjacent its outer end.

The section of the shaft I66 adjacent the shaft I8I has a sleeve I 69 splined thereon which con- A driving connection between the clutch members I65 and I69 is provided by a series of interleaved discs I10, drivingly connected alternately with Shifting f the movable collar is effected by a clutch shifting member I19 slidably on the sleeve I69 and disposed in abutting relation to. the collar I12.

Encircling the other section of the shaft I69 by external teeth formed on a shlftable clutch member I 89 splined to the shaft I66 intermediate the end'sthereof. The clutch member I 88 constitutes the driven member of the clutch I22 previously referred to.

The clutch members I13 and I95'are adapted to be shifted by a common actuator to drivingly couple either the rapid traverse motor M or the slow feed motor M with the shaft I69 selectively or to disengage both clutches and thus interrupt rotation of the shaft. In the preferred form shown in Figs. 8 and 14, the clutch actuator is of the pressure fluid operated type and comprises a pair of cylinders I99 and I99 mounted in parallel relation upon a plate I9I adapted to be secured to one side wall of the housing I69. 'Pisperipheral grooves in the clutch members I19 and I69.

Introduction of pressure fluid into the inner ends of both cylinders I99 and I99f forces the associated pistons I92 and. I92 to the extreme left position (as viewed in Fig. 14) thus shifting the'rod I95 to-the left. In this movement the rod I95 shifts the clutch member I13 to engaged position and at the same time withdraws the clutch member I89 to disengaged position. The

rapid traverse motor M is therefore effective to drive the shaft I99.

Introduction of pressure fluid into the outer ends of both cylinders forces the pistons to their extreme positions in the opposite direction.

thereby engaging the driving and driven members of the clutch I22 and disengaging the clutch I2I. Slow feed motor M is then efiective to drive the shaft I99 at a rate determined by the setting of the hydraulic transmission I-I. Introduction of fluid into the forward end of one cylinder and into the rear end of the companion cylinder shifts the pistons to the positions shown in Fig. 8 whereby the shifter rod I95 is moved to an intermediate position and both clutches are disengaged.

The feed selector unit 13 is mounted on the saddle 39 at'the rear of the unit A and extends transversely across the saddle which is recessed as at I99 to accommodate the saddle traversing shafts as shown in Fig. 16. The unit includes a box like frame 299 having a series of transverse vertically disposed webs for supporting the intermediate shaft I24 and the shafts I29 and I39. As willbe seen by reference to Fig. 16 the worm wheel I29 is keyed to the central portion of the shaft I24 and the shaft is provided at opposite ends with toothed members 29! and 292 con-. stituting, respectively, the driving elements of clutches I21 and I28. The driven member of the clutch I21 comprises a sleeve 293 splined to the shaft I29 which is supported on the housing 299 in axial alinement with the shaft I24. Shaft I39 is also axially alined with the shaft I24 and supported in suitable bearings carried on the housing 299. A sleeve member 299 splined to the shaft cooperates with the clutch member 292 and comprises the driven element of the clutch I29. Clutch members 299 and 294 are mechanically interconnected by a clutch shifting rod 295 (Figs. 8 and 15) having fingers 296 and 291- engaging in peripheral grooves in the respective clutch members. The clutch shifting rod is actuated in the same manner as the corresponding element of the actuator for the clutches IN and I22. More particularly, a yoke 296 pivoted intermediate its ends on the rod 295 is connected at opposite ends by piston rods 291 and 291 with pistons 299 and 298 operating in parallel cylinders 299 and 299' attached to a side wall of the housing 299. By shifting these pistons individually or together, the clutches may be engaged selectively or set in a neutral disengaged position to interrupt the drive.

Disposed'in the recess I99 in the saddle immediately below the selector unit B is a frame 2I9 adapted to support the shaft I39. Worm 4 shafts I31 and I39 each journaled in separate frames 2 and 2I2 are coupled to opposite ends of the shaft I39 by means of couplers 2I9 and 2 I4 of conventional type. Accurate alinement of the various shaft supporting frames is facilitated by the provision of keys M5 on each frame cooperating with a complementary keyway M9 in the bottom of the recess I99.

The manner in which the vertical pinion shafts I39 are supported in the saddle 99 will be readily seen. by reference to Fig. 17 of the drawings.

Thus, the saddle is formed with recesses I99 communicating with the recess I99 at one side of each of the worm shafts I9? and I99. An upstanding hub ZII within each recess I99 provides seats for spaced anti-friction bearings 2I9 for the shaft I99.

The machine elements enclosed in the units A and B above described and the saddle driving mechanism are protected from entry of dirt or other foreign material by means of suitable cover plates of sheet metal or the like. Thus, the housing for the unit A is closed at its upper end by a cover 2I9 (Fig. 14) while the frame structure of the unit B is closed by cover sections 2I9 and 2I9'. The unit B extends over and covers a substantial portion of the recess I99 while the section in which the frame 2I2 is located is closed by a cover plate 229. Suitable cover plates 22I encloses the recess I99 in which the pinion shafts I39 are located. v

As mentioned hereinbefore, the drive for the table includes a reduction gear mechanism C in-- terposed between the shaftI33 and the vertical table driving shaft 65. Referring to Fig. 18, it will be observed that the shaft I33 is connected by a coupling 222 with a horizontally disposed shaft 223 having a pinion 224 meshing with a pinion 225 on a parallel shaft 226. A bevel gear 221 fast on the shaft 229 engages a bevel gear 228 fast on a vertical shaft 229 which has a small I clutchactuator.

pinion 230 meshing with a large gear 231 on a companion vertical shaft 232. Shaft 232, in turn, has a small pinion 233 meshing with a large gear 234 on a vertical shaft 234'. The gear 234 also meshes with a gear 235 on a shaft 236 drivingly connected with the vertical shaft 65 by a suitable coupling 231. The various shafts are supported on anti frictiOn bearings on a housing 238 adapted to be bolted to the face of the saddle for the hydraulic transmission H is mounted on one side of the transmission within the sub-base of the supporting structure. In order to provide a visual indication of the setting of the hydraulic transmission, a suitable dial type indicator 240 (Fig. 1) is provided on the hand feed unit E and operatively connected with the regulating motor. The connection, provided for this purpose includes a vertical shaft 24! (Fig. 16) drivingly connected with the transmission ad.- justing shaft by a bevel gear 242 and having at its lower end a spiral gear 243 arranged to drive a horizontal shaft 244. Shaft 244 extends into the housing of the unit E and has the indicator 240 attached to its projecting end within a re cess 245 in the wall of the housing. This recess is closed by a transparent coveror window 245'.

The housing of the unit E is also formed to provide a compartment 246 immediately behind the indicator recess 245 for a pair of limit switches LS and LS suitably interconnected with the regulating motor RM so as to limit the range through which it is permitted to turn the transmission adjusting shaft. These limit switches are adapted to be operated alternately by radially projecting switch operating fingers 241 and 248 fixed on the shaft 244 within the compartment 246. For convenience of access a switch S for starting and stopping the motor RM may be mounted on the housing of the unit E closely adjacent the indicator as shown in Fig. 1. o

The hydraulic system for the clutch actuators and table and saddle clamps is shown diagrammatically in Fig. 8. Fluid such as oil is drawn from a sump or reservoir R through a filter F and delivered under pressure into a header 256 by a pump P which may be of any suitable type.

A relief valve 251. connected with the header ,prevents excessive pressures from developing in the system. Pipes or ducts lead from the header to a series of conventional two-position control valves which direct the fluid to'the cylinders of and 251 control the delivery of fluid to the cylinders 203 and 203' of-the feed selector clutch actuator.

The control valves are preferably adapted to In a like manner valves 256 be operated by solenoids so that their setting may be readily effected by remote control. Moreover the electrical circuits for the solenoids may be interlocked in well-known manner so that the operation of the actuators in the proper sequence is insured.

Apressure lubricating system is also provided for insuring adequate lubrication of all bearing surfaces 'in the work supporting structure. As shown in Fig. 8, a pump P is arranged to draw lubricating fluid such as oil from a reservoir B. through a filter F and deliver it under pressure through a duct 260 to a control valve 26!. One

branch line leading from the valve carries oil to the table supports I00. Another branch line delivers oil to the speed reduction gear unit 0, the table driving worm 64, and the bearings of the table spindle 39. The latter branch is provided with a check valve 262 to prevent reverse flow of oil. Oil pressure in this system is controlled by a suitable relief valve 263.

A second pump P" arranged to draw oil from the reservoir B. through a filter F" delivers the fluid under pressure to a line 265 which has one branch leading to a valve 266 controlling the flow of fluid to the feed selector unit B and to the ways 3|. Another branch of the line 265 extends through a check valve 261 to the feed and rapid traverse selector unit A. A relief valve 268 controls oil pressurein this system.

The valves 26l and 266 are preferably solenoid operated and their energizing circuits may be suitably interlocked with the circuits of the valves of the hydraulic system so that oil will be delivered to the proper machine elements when such elements require lubrication.

In the exemplary machine, the pumps P, P, and P" are adapted to be driven by a common motor The pumps and motor may be conveniently assembled as a unit on a frame 216 adapted to be bolted to one side of the saddle 36 as shown in Fig. 3. Suitable recesses in the saddle closely adjacent the pumps form the reservoirs R and R.

It will be apparent from the foregoing that the invention provides a work support of novel and improved construction, particularly suitable for vidual bed to adapt it for use withfloor type boring, drilling and milling machines. The table supporting frame work, drive mechanism and other parts are all. of sturdy construction and enable the supporting structure to be used with extremely large workpieces and for what is commonly known as heavy duty service. The varlens elements of the drive mechanism are constructed in the form of simple compact units to facilitate manufacture and initial assembly and likewise simplify the removal of such elements for; replacement or repair.

The invention also provides novel means for positively clamping the movable elements of the supporting structure against undesired movement I and meansfor supporting the peripheral edge of the rotary work table so as to prevent deflec. tion of the table under load.

traverse motor with said driving mechanism, a

We claim as our invention:

1. A work support comprising, in combination,

. riage on the ways, other driving mechanism operative to rotate the table, a rapid traverse motor,.

a slow feed motor, a main drive shaft, a clutch operative when engaged to drivingly connect the rapid traverse motor with said shaft, a second clutch operative when engaged to drivingly connect the slow feed motor with said shaft, a third clutch operative when engaged to drivlngly connect said shaft with one of said driving mechanisms, a fourth clutch operative when engaged to drivingly connect said shaft with the other of said driving mechanisms, a remotely controlled power driven actuator for said first and second clutches, and a second remotely controlled actuator for said third and fourth clutches, said actuators being operable to engage the clutches selectively or to disengage all of the clutches.

2. A work support comprising, in combination, a carriage adapted to travel on horizontal ways, a frame secured to said carriage, a work supporting table rotatably mounted on said frame,

driving mechanism operative to traverse the carriage on the ways, other driving mechanism operative to rotate the table, a rapid traverse motor,

a slow feed motor, a main drive shaft, a clutch operative when engaged to drivingly connect the rapid traverse motor with said shaft, a second clutch operative when engaged to drivingly connect the slow feed motor with said shaft, a third clutch operative when engaged to drivingly connect said shaft with one of said driving mechanisms, a fourth clutch operative when engaged to drivingly connect said shaft with the other of said driving mechanisms, 2, pressure fluid operated actuator for said first and second clutches, a second pressure fluid operated actuator for said third and fourth clutches, and valve means for controlling the delivery of pressure fluid to said actuators.

3. A' work support comprising, in combination,

a carriage adapted to travel on horizontal ways, a frame secured to said carriage, a work supporting table rotatably mounted on said frame, driving mechanism operative to traversethe carriage on the ways, other driving mechanism operative to rotate the table, a rapid traverse motor, a slow feed motor, a main drive shaft, clutch means engageable selectively to connect either of said motors with said shaft, and other clutch means engageable selectively to connect said shaft with either of said drive mechanisms.

4. A work support comprising, in combination, a carriage adapted to travel on horizontal ways, a frame secured to said carriage, a work sup porting table rotatably mounted on said frame, driving mechanism operative to traverse the carriage on the ways, other driving mechanism operative to rotate the table, a'rapid traverse motor, a slow feed motor, and means operable to connect either of said motors with either of said driving mechanisms selectively.

5. A work support comprising, in combination, a' carriage adapted to travel on horizontal ways, a column like frame rising from the carriage, a

second clutch operative when engaged to connect said slow feed motor with said driving mechanism, and actuating mechanism common to said clutches operable selectively to engage either clutch individually or to disengage both clutches.

6. A work support comprising, in combination, a carriage adapted to travel on horizontal ways,

' a frame secured to the carriage, a work supporting .table rotatably mounted on said frame, driving mechanism operative to rotate the table, a rapid traverse motor on said carriage, a slow feed motor on said carriage, a clutch operative when engaged to connect said rapid traverse motor with said driving mechanism, a second clutch operative when engaged to connect said slow feed motor with said driving mechanism, and actuating mechanism operable to engage and disengage said clutches selectively.

7. A work support comprising, in combination, a carriage adapted to travel on horizontal ways, a frame secured to the carriage, a work supporting table rotatably mounted on said frame, driving mechanism operative to rotate the table, a

rapid traverse motor on said carriage, a slow feed motor on said carriage, clutch means engageable selectively to couple either motor to said drive mechanism, and remotely controlled power driving means for actuating said clutch means.

8. A work support comprising, in combination,

a carriage adapted to travel on horizontal ways,

a frame secured to the carriage, a work supporting table rotatably mounted on said frame, driving-mechanism operative to rotate the table, a rapid traverse motor on said carriage, a slow feed motor on said carriage, and means operable to connect either motor to said drive mechanism selectively.

9. A work support comprising, in combination, a carriag adapted to travel on horizontal ways, a column like frame rising from said carriage, a work supporting tablev mounted on said frame for rotative movement, and power drive means means supporting the periphery of the table to work supporting table rotatably mounted on said prevent deflection under load comprising, a track on the rear face of the table concentric with its rotational axis, a shoe supported on the frame in a position to engage said track, and means yieldably urging said shoe against the track.

11. The combination with a work supporting table rotatably mounted on a stationary frame, means supporting the periphery of the table to prevent deflection under load comprising, a track on the rear face of the table concentric with its rotational axis, a shoe having a flat bearing surface, means on the frame supporting the shoe with the bearing surface positioned for engagement with said track, and spring means yieldably urging the shoe against the track, said spring means being adjustable to regulate the pressure exerted by the shoe on the track.

12. The combination with a work supporting table rotatably mounted On a stationary frame, means supporting the periphery of the table to prevent deflection under load comprising, a track on the rear face of the table concentric with its a rotational axis, a shaft supported on the frame to rock about an axis substantially parallel to

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