US2478562A - Grinding machine - Google Patents

Description

Aug. 9, 1949. G. w. BINNS ET AL GRINDING MACHINE Filed March 12, 1947 7 Sheets-Sheet 3 xxx ii I m auanwwnqsh 4..

I III I I INVENTORS 650565 w B/N/VS By FFEJfF/CA 5' 1607/45 1949- G. w. BINNS ET AL 2,478,562

GRINDING MACHINE Filed March 12, 1947 7 Sheets-Sheet 4 INVENTORS 650264- M BIN/v.5 y fPfPEF/C'K 5/1 6045 flTTOF/VEYS Aug. 9, 1949. G. w. BINNS ETAL 78,56

GRINDING MACHINE Filed March 12, 1947 7 Sheets-Sheet 6 HTTOEA/EYS Patented Au 9,1949v GRINDING MACHINE George W. Binns, Cincinnati, and Frederick S.

Haas, Orgonia, Ohio, assignors to The Cincinnati Milling Machine 00., Cincinnati, Ohio, a

corporation of Ohio Application March 12, 1947, Serial No. 734,080

33 Claims. 1

The invention relates to improvements in grinding machines and has particular reference to machines for the production of surfaces of revolution.

One of the objects of the present invention is the provision of a grinding machine particularly adapted for generation of external surfaces of revolution.

A further object of the present invention is. the provision of a machine of this character having interrelated parts constructed and arranged to effect an automatic continuous cycle production of duplicate work pieces.

Another object is the provision of a machine in which the formed surface of revolution shall be in predetermined relation to a. preformed terminal portion of the work.

An additional object of the invention is the provision of a machine which will effect automatic accurate positioning of successive work pieces for corresponding action of the grinding wheel with respect thereto.

Another object of the invention is the provision of a simplified structure adapted for use in connection with various grinding machines but especially in connection with machines of the type herein illustrated vand described which will facilitate the accurate varying of the height or relationship of the work axis to the grinding wheel axis without disturbing the rigidity of mounting or the relationship of the other elements of the machine.

The invention further contemplates the provision of simplified means for accurately effecting the multiplicity of adjustments essential for precision production of work accurate to a fractional part of .0001".

Other objects and advantages of the present invention should be readily apparent by reference to the following specification, considered in Figure 9 is a similar view illustrating the position occupied by the parts operation Figure 10 is a fragmentary front elevation illustrating the automatic work clamping mechamsm.

during. the loading Figure 11 is a horizontal section as on the line ii-ii of Figure 3.

Figure 12 is a fragmentary View of the compensator portion of the work clamping mechanism.

Figure 13 is a diagrammatic view of the hydraulic circuit and controls therefor.

Figure 14 is a diagram of the electrical 'con-- trols for cyclic operation of the machine. and

Figure 15 is a fragmentary sectional view as on the line I5i5 of Figure 2.

In the drawings inwhich similar characters of reference are employed to denote corresponding parts throughout the several views, the numeral 20 designates the 'base or bed of the maconjunction with theaccompanying drawings forming a part thereof and it is to be understood that any modifications may be made in the exact structural details there shown ,and described, within the scope of the appended claims, without departing from or exceeding the spirit of the invention.

Figure 1 represents a plan view of a machine constructed in accordance with and embodying the principles of this invention. 4

Figure 2 represents a transverse vertical sec-' tional view taken as on the line 2 -22 of Figure 1. Figure 3 is a. longitudinal vertical sectional view as on the line 3-3 of Figure 1.

chine which is of conventional hollowor ribbed form.

Rising from the bed is a platform 2! on which is rigidly mounted the grinding wheel base 22 having a trunnion 23 oscillatablysupporting the swinging grinding wheel unit 24. This unit, as' indicated in Figure 1, includes the'spindle'25 for grinding wheel 26 and a motor unit 21 operatively connected with the spindle 25 as by the series of driving belts 2 8.

The bed is further provided in subtending relation to the forward portion of the grinding wheel unit withyvertical ways as at 29' formed on ther'ib 30.- Rib 30 is additionally slotted as at 3| to receive guide block 32 oscillatably supported in the slot by trunnion 33. I A substantially L-shaped intermediate bed plate 34 has an elongated narrow portion which extends lengthwise of the bed 20 and has a surface or way 35 interengaged with one, of the ways 29, being held inclose interfitting engagement therewithas by the adjustable taper gib 36 engaging the way onthe opposite/face of the rib and locked to the member 34 as by the adjusting screw 31.

At the left hand portion of the machine, as viewed in Figures 1 and 3, the supplemental bed portion is of increased width as indicated at 38 and provides a support for the work supplying, holding, and driving mechanisms as hereinafter described.

By reference particularly to Figures 2 and '7 it will be noted that extending transversely of the main bed unit 20 is a shaft 39 rotatably jour-b that this rotary adjustment of shaft 39 by varying the position of cam portions 42 and 43 will correspondingly raise or lower the upper effective surfaces 48 and 49 of the discs 44 and 45. Disc 44 extends upwardly through slot 50 in auxiliary guide rib 5|, and disc 45 correspondingly extends upward through slot 52 in the main guide rib 30 for the supplemental bed. Rotary adjustment of shaft 39 by raising or lowering of discs 44 and 45 will effect corresponding movement of the widened portion 36 of the supplemental bed unit riding thereon, the unit as an entirety oscillating about the supporting trunnion 33.

In order that the supplemental bed unit and parts carried thereby may be longitudinally adjusted on the bed, and therefore with respect to the grinding wheel 26, member 32 is threaded to receive adjusting screw 53 whose outer end is swiveled in plate 54 carried by the right hand end of the supplemental bed. Secured on the projecting portion 55 is a cupped plate 56 provided with an actuating handle 51 for rotation of the plate and adjusting screw. This cup is formed with the internal gear 58 with which meshes pinion 59 on adjusting screw 60 which extends longitudinally of the bed and has mounted on its opposite end the adjusting hand wheel 6|. By this construction the longitudinal movement of the supplemental bed with respect to the main bed may be effected by the operator from either the right or left hand end of the machine.

It will be apparent that the present machine is primarily intended for plunge cut or infeed grinding, that is to say, operations in which the grinding or stock removal is eifected by relative shifting of the work and grinding wheel in a direction one toward the other as distinguished from intermittent relative advance of the parts with additional relative traverse as in the production of long cylindrical or like surfaces. It will be understood, however, that the principles of the invention as hereinafter described are equally applicable to machines employing not only infeed but also relative traverse of work and grinding wheel during the machining operation. In the form chosen for purposes of illustration, means have been provided for insuring absolutely accurate positioning of the work for performance of the grinding operation and additional means for shifting the wheel in a direction toward the work for performance of the grinding operation.

In this embodiment, the mechanism for adjust-- ment of the supplemental bed is therefor em ployed only for the accurate setting up or positioning of the work although it will be understood that it could be additionally employed for effecting the relative feeding movement between work and grinding wheel if so desired.

It is to be particularly noted that the supplemental bed or table member is fully guided by the interengagement of the ways on the underside of the member with the rib of the bed to prevent any movement of the parts so that the table is shiftable in a direct linear direction on the bed. It will further be noted that the arrangement of the parts is such that adjustment of the eccentrically supported rollers 45 effects an upward tilting movement of the table member for effecting a raising or lowering of the work piece supports, and thus the work piece with respect to the periphery of the grinding wheel for varying the radial contact position of the work with the grinding wheel. When so adjusted by the members 45, the longitudinal shifting of the table member 34 will be substantially along this radial line and at an angle to the horizontal plane of the bed, thus maintaining the relative relationship of the operative face of the grinding wheel and the work piece for different longitudinal adjustments of the table.

Work positioning mechanism The present machine is particularly adapted for the performance of grinding operations in accordance with the principles disclosed in pending application, Serial No. 662,191. Being intended for the production of work of a high degree of accuracy, it is essential that the work supporting device be capable of minute accurate adjustments in a multiplicity of directions, and at the same time with a simplification of parts, facilitating manufacture and reducing to a minimum the possible error introducible by employment of undue multiplicity of slides. In attainment of this result, the Portion 36 is provided with an arcuate T slot as at 62 to receive the head of the guide and locking stud 63 mounted in slide block 64 adjustably fitting within recess 65 of the work unit bed plate 66.

The bed plate is further provided with a pivot stud 61 interfitting with guide block 68 slidable in recess 69 of the bed plate unit 66.

By reference to Figure 2 it will be noted that tightening of clamp screw 10 will draw stud 61 downward, thus securely locking the block 68 in place, while loosening of screw 10 will permit of swinging of 66 about said stud as a pivot. Similarly, tightening of clamp screw H will lock block 64 and stud 63 in position against arcuate movement as guided by 62 while loosening of this clamp will permit the unit 66 to be swung as an entirety about the pivot 61. This angular adjustment makes possible a lining up of the work holder mechanism in absolute parallelism of the base unit 66 with respect to the fixed posi- 3 tion determining members 63 and 61 without in any way varying the angular setting which has been affected. This is accomplishable in that with the stud 63 locked in position by screw H, loosening of the nut 12 will free the clamping maybe moved relative to the locked stud 99 to the extent permittedby slot 14 and recess 95.

Carried by member 99 is the screw adjusting mechanism 19 shown at the right hand portion of Figure 2, terminating in the screw .16 engaged with block 68. It will thus be seen that with both the pivot stud 01 and the T slot stud securely locked in place with respect to the bed v98, a limited adjustment maybe imparted to the bed plate 66.

Mounted upon the bed plate 68 are the work driving and the automatic-work feeding and holding mechanisms. The work driving mechanism includes a slide 11 guided for transverse movement by the rib 18 and securable in adjusted positions as by the guide and clamp studs I9, a clamp screw 90 being shown and'cooperating with one of the studs 19 for clamping thereof. This transverse adjustment is preferably effected by a screw 8I swiveled in bracket 92 carried by the slide and in threaded engagement with nut 83 mounted in the bed plate 00. A suitable pilot wheel 84 facilitates rotation of the screw.

spindle 85 driven as through belts 86 by motor 91.

This spindle has mounted thereon the precision bearing collar 99 engaging the face89 of the slide 11 to insure true running of the outer end of the spindle which is provided as with the abrasive cup or work driving member 90. A truing device 9| mounted on bracket 92 of the work holder is projectable to engage and form accurate terminal surface on the member 90.

Mounted on the bed plate 09 for adjustment relative thereto as by loosening of the bolt 93 is the bracket 94 to which the member 92 is secured as indicated in Figure 2. This bracket is provided with a segment 95 formed with T slot 96 to receive the bolts 91 and 98 for securing at any desired vertically and angularly adjusted position the work engaging shoes 99 and I00 respectively. These shoes are preferably positioned as described in co-pending application, Serial No. 662,191, so that the angled upper face of the shoe element I00 engages the peripheral portion of the work to be ground at a point closely adjacent the point of contact of the grinding wheel 26 therewith, while the shoe 99 engages the work at the opposite side of its axis from the shoe I00, the two together forming a trough in which the work may be rotated by the frictional driving engagement of the face of cup 90 therewith and being so relatively positioned as to prevent displacement of the work by the component thrust reactions of the rotary driving member and the grinding wheel thereagainst. It will be understood that in practice the shoe determined axis of the rotating work piece is displaced in a direction downwardly and toward the grinding wheel as respects the axis of rotation of the driving member so that the driving member will exert a rotary and downward thrust component on' the work, tending to maintain it in engagement with the shoes both prior to and during the grinding operation.

For automatically successively supplying work .pieces in corresponding grinding position in themachine and subsequently ejecting the completed work pieces, the bracket 94 is formed with ways IOI guiding a vertically reciprocating slide I02 coupled as by rod I09 with actuating piston I04 reciprocable in cylinder I05 carried by the'bracket.

The slide I02 has a central slot I08 of width to clably greater .lengththan thediameteroi the workpieces.

At its lower end it is provided with the tra 5 verse angularly disposed carrier plate I01, providing a carrier. and limiting stop for the work piece such as I08. It is further provided with a lateral gate or work piece movement limiting member I09.

The'oper'ation of these parts will be best understood .-by a comparison of Figures 8 and 9. In Figure 8 the slide is shown in raised position. In this position the laterally extending pin IIO engages collar III on the spring depressed stop readily adjusted for suitable engagement with] different diameters of work pieces.

In this position of the parts, while the stop member H4 is raised, permitting the innermost of a series of work pieces to move inward by gravity in the trough I I5 secured to the side of bracket 94, the gate I09 extends transversely of the discharge end of the trough, holding back the innermost work piece. At this time the carrier plate I01 is substantially aligned with the discharge trough II6 so that the work piece I08a just completed will roll by gravity from member I01 into the trough. For convenience of assembly and operation, this trough has been shown mounted as through the medium of adjusting bolt H1 in suitable position on the segment 95.

As the plunger or slide I02 is lowered through the intermediate position shown in Figure 9, the

ward movement of the plunger to the D sitionshown in Figure 3 will place the carrier plate I01 at a point below the effective work grinding position as determined by shoes 99 and I00 so that the work will rest freely on these shoes and the carrier plate will be out of engagement therewith. On reverse movement of the parts, the carrier will again lift the work piece from the supporting shoes into the position indicated by I08a, Figure 9, so that the work piece can be discharged and upon reverse movement a new work piece will be placed in position. I I To retain the work during the grinding operation there has been shown pivoted to the member 94 as at II8,'the clamp arm II9 having at its upper end roller I20 engageable by cam I2I carried by the plunger I02. As the plunger reaches lowermost position, this cam presses roller I20 and thus the upper portion of the arm outward, swinging the lower cylindrical portion I 22 thereof inward against the retracting action of spring I23.

The cylindrical portion I22, as will be best understood by reference to Figures 11 and 12, has

7 slidably keyed therein bushing I24 locked in axially adjustable relation to the cylindrical portion I22 as by the disc nuts I25. Slidable within this bushing is the member I29 pressed inwardly or in the direction of work engagingmember 7 by spring I21 whose pressure may be variably de.

termlned by adjustment of screw I28. Cross pin I29 riding in slots I30 of bushing I24 prevent rotation of I25 within I24. Member I26 is bifurcated or slotted as at I3I to receive the threaded stud I32 swiveled on pin I29 and bearing the pair of rollers I33 and I34 for engagement with face of a work piece I08 whereby the same is resiliently held against member 90 in a manner to permit it automatically to conform to the face thereof.

In order that the clamp device may be readily adapted for use in connection with different diameters of work pieces, the rollers I33 and I34 may be axially adjusted along stud I32 and secured in said adjusted position by nuts I35.

It will thus be seen that when the work piece is deposited in position upon the supporting shoes 99 and I the continued downward movement of the work delivering slide will, through cam I2 I, swing arm I I9 to effect a resilient clamping of the work piece against the work driving member.

Conversely, the initial retracting or upward movement of the work delivery plunger will release the cam pressure, when spring I23 will move the clamp into disengaging position, leaving the work piece free to be elevated to the discharge position by engagement of member I01 with the work, as shown by the dotted line work piece I08a in Figure 8.

The grinding wheel unit In the form of the invention shown for purposes of illustration, the grinding wheel has been indicated as movable in a direction toward and from the accurately positioned work piece for performance of the grinding operation. While this movement could be effected by a direct linearly moving slide or the like, it has been found preferable for accuracy of performance and cyclic control to mount the grinding wheel unit 24 on the trunnion 23 which is secured in fixed position with respect to the bed 20. The unit 24 includes a cylindrical portion I35 providing the hydraulic cylinder I31 in which is slidably mounted piston I38 having a projecting abutment rod I39 at one end and a recess or socket I40 at the other. To facilitate adjustment of the stroke or movement of piston I38, there is preferably provided within the cylinder intermediate the piston and cylinder wall a sleeve I4I which may be adjusted axially in a downward direction in the cylinder by means of screw I42. This sleeve is provided with the cap I43 having abutment lug I44 for engagement in the recess I40 of piston I38, the position of the sleeve and its abutment lug variably limiting the upward movement of piston I38. Intermediately connected to I36 is the hydraulic conduit I45 communicating at one end with a control valve I45, and at the other 'with the interior of the cylinder I31 and by way of circumscribing groove I41 and port I48 with the interior of the sleeve. In this manner the reaction of hydraulic pressure between the cylinder cap and end of the piston may be variably determined by positioning of valve I46, while the projecting abutment lug I44 insures that there will be at all times an inlet clearance at port I48 between the sleeve cap and piston so that the hydraulic pressure may properly react as respects the parts.

At its lower end rod I39 engages the rounded anvil 0r abutment lug I49 carried by one armof the lever I50 which is of substantially T-shape or double bellcrank formation having a lower depending arm II engaging an adjustable abutment I52 carried by piston I53 and a second laterally extending arm I54 interengaged with the abutment piston I55.

It will be noted that the piston I53 is of relatively large diameter as respects pistons I38 and I55 and is shiftable toward the right in cylinder I55 as by hydraulic pressure introduced through conduit I51. Movement of the piston to the right will correspondingly rock the lower end of lever arm I5I to a position which may be adjustably limited by the stop I58 in threaded engagement with bracket I59 on the bed 20 which has a terminal abutment portion I60 slidable through bracket I5I and engageable with the face I62 of lever arm I5I. Introduction of pressure into the chamber I83 of sleeve I4I, due to the relative small diameter of the parts will cause a rapid movement of piston I38 to the position shown in Figure 7, thus rocking the wheel unit'counterclockwise about trunnion 23 moving the wheel in the direction of the work. Subsequent movement of piston I53 toward the right at a feed rate as determined by throttle I64 will then cause a slow continued feeding movement which is controlled by the resistance of the back pressure or hydraulic spring effect produced by introduction of pressure through conduit I65 into chamber I66 where it reacts on piston I55 urging same upward against portion I54 of the rock lever.

To limit the amount of this feeding movement or oscillation of the wheel head unit 24, it is provided with a bore or guiding passage at I61 within which is slidably mounted the stop bar I68 keyed against rotation relative to the bore as by plunger I69. This stop bar has a shouldered portion or head I10 at its lower end underlying the abutment III of unit 22. At its upper end member I68 has an internally threaded bore I12 receiving adjusting screw I13 swiveled in cap unit I14 which ma be provided with graduations as at I15 to denote adjusted position of the stop. A hand wheel I15 facilitates adjustment of the screw and thus of the stop position. Formed axially of the adjusting screw and stop bar are aligned passages to receive the locking rod I11.

A clamping screw I18 threaded into the upper portion of the adjusting screw serves to force this rod downward so that its beveled end I19 will react against face I of lock plunger I8I which, in turn, reacts against the lower portion" of the stop guide, positively to lock the guide in its adjusted position.

Machine operation The manner of automatic cyclic operation of the machine will be best understood by reference to diagrammatic views I3 and I4, the hydraulic actuating and control devices being particularly illustrated in Figure 13 and the sequentially functioning electrical devices and related circuits in Figure 14. As shown in Figure 13, there is provided a reservoir I82 from which pump I83 is supplied with suitable hydraulic medium to create a volume of fluid in supply line I84 under a pressure determined by relief valve I85. The electrical system, as indicated in Figure 14, may be considered for purposes of understanding of the invention as including the main electrical supply leads I85 and I81. When the machine is to be operated, stop switch I88 is in normally closed position, and starting switch I89 is temporarily closed to energize the hydraulic pump control relay I98 maintained in continuing operation by the controlled switch I9I At the same time, the control relay I92 for the grinding wheel The closing of these switches also energizes the conductor I94 extending to the cycle control mechanisms. This conductor includes a normally closed cyclestop switch I99 and normally opened temporary manually closable cycle start ing switch I99 Upon closing or the cycle start switch- I99 line I91 to controller CRI .for cyclic operation is energized, closing and maintaining closed the switch er I As a result, the circuit from I99 will be maintained closed to I91 by way of I98 after release of the cycle starting switch I99. At the' same time, lead I99 is energized from I91 while lead 299 is activated through 29l irom'the cycle starting switch, thus energizing control relay CR2 and closing switches 012 and cr2'-. The closing of switch 012 completes the circuit through 292, energizing control relay CR9 which closes switch or! and also-causes activation of solenoid 299, which is coupled with valve element 294. When deenergized, spring 299 maintains valve in the position shown in Figure 13in which pressure fluid from I94 may be discharged b wayof the valve spool 299 and conduit 291- into the lower end of cylinder I99, raising piston I94 and the work controlling slide I92 to the position shown in Figure 8.

When the solenoid 299 is energized, groove 299 connects conduit 291 with discharge or reservoir conduit 299 while groove 299 couples pressure conduit I94 with conduit 219 at theupper end of the cylinder, moving the piston I94 and associated parts into the depressed or work loading position shown in Figure 3. In this manner a work piece is automatically placed in position in the machine and there secured by the spring pressed clamp rollers I39 and I 94 as previously described. I Plunger I92 is diagrammatically shown as provided with the-switch operating arm 2 which, when the plunger reaches its upper end of movement, holds limit switch LSI in closed position. During, cyclic operation of the machine 45 like incident to-employment of ordinary adjusting slides and screw or other actuating mechanisms.

each time that the plunger is raised, if cycle selector switch 29I is closed, operation of switch 2 II will energize relay CR2 as just described for its energization by closing-of cycle starting switch I99. In either event upon the completion of this circuit a holding circuit for CR2 is established through the closed side of LS3A and cr2' and conductor 2I-2.

As the plunger moves downward through work loading position arm 2 contacts and closes 10 closes and holds" in' closed positiomthe spring openable limit switch LS9. In its open position LS9 through LSIA and 01-2 completed the holding circuit from I99 to'2I2 tor CR2, but as LSSA 5 is'opened and LSlB is closed, CR2 is deenergized.

opening the holding circuit through 012 for CR9. Alternatively, however, this holding circuit has been completed through LS2, cr4-cr9 and 292 so 1 that CR9 and solenoid 299 remain energized.. At 10 the same time, completion of. the circuit through LS9B energizes control relay CR9 for activation of solenoid 2 I 9.- This solenoid 2I9 is coupled with valve 229 normally urged as spring 22I into position to couple conduit I91 by way of 222, groov 223, and return conduit 224 to reservoir.

However, when solenoid 2I9 is energized, this valve will be raised, coupling pressure conduit I94 byway 01' valve groove 229 to conduit 229, and thence through pressure control valve 221 and b variable throttle m to conduitfl91 for introduction of fluid at a throttle determined rate into cylinder I99. In this position of the parts the lower portion 01' the .valve closes oi! reservoir connection 224 from 222 and the hydraulic actuatin 25' medium 'flows through throttle I94 into cylinder I99. The large'terminal area of the piston facilitates extreme accurate control oi. rate or feeding movement by throttle I94.

The feeding movement of the grinding wheel,

as has been described, is limited by interengagement of stop flange I19 with abutment I1I ir respective oi. the ultimate relative movements of the actuating pistons and intermediate motion transmitting element I99. After the parts I19 and Ill have been positively interengaged, due

to the greater piston diameter, and thus total eflective pressure within cylinder I59, continued movement of piston I 59 .to the right willforce .pistonl99 up in its cylinder, backing out actu- 40 ating pressure through conduit I45.

For-final termination of the grinding operation use is preferably made of an automatic timing device which may be-set in operation either by limit switch LS9 or by the additional limit switch LS4, the latter having been indicated in diagrammatic view, Figure'14. This limit switch LS4 is carried by the bed 29 in position to be engaged limit switch LS2 and through leads 2I9, 2, and as by arm 229 on member 99. Closing of this spring 2 I 1. Upon energization of the solenoid the valve movesydownward, closing off the connection with 299 and coupling pressure conduit I94 with conduit I49 whereby unrestricted pump pressure is introduced into the space I41. As rod I39 is firmly seated against I49 in its depressed position, as shown in Figure 13, the introduction of this pressure will swing the unit 24 in a counterclockwise direction until piston I38 reaches its limit of movement as indicated in Figure '7, this effecting a rapid approach or "rapid traverse" infeed movement of the grinding wheel. Member 24 is provided with the switch actuating arm or cam 2l9 which, as the unit 24 moves upward,

1 switch completes a circuit from 2I3 by way of 229 and 239 to the tarry timer relay TRI, which may be of conventional commercial type, either hydraulic or electrical, and which, a predetermined period after its energization, opens the normally closed switch trI in the lead 2I4 to CR4 controlling solenoid 2l5 for reversal of hydraulic actuating conditions as respects the piston I38. Upon functioning of the tarry timer mechanism solenoid M5 is deenergized, when piston valve 2I9 will be restored to the position shown in Figure 13 by spring 2", coupling conduit I45 to reservoir when the weight of the right hand portion of unit 24 will oscillate same in a clockwise direction, rapidly retracting the grinding wheel with respect to the work. This movement releases limit switch LS3, opening the holding circuit of CR5 and deenergizing solenoid 2I9. Spring 22I moves valve 229 to the position shown in Figure 13, shutting oil pressure from 229, and

at the same time couples ISL-222 to reservoir through groove 223 and conduit 224. This bypasses throttle I64 so that the rapid movement of 24 may continue, reacting through the bellcrank lever l50-to restore piston I53 to the position shown in Figure 13.

The holding circuit cr2 and 012' having been previously deenergized, as described, the remaining holding circuit for CR3 in effect has been through 2l3, 229 and the series disposed switch elements 013 and 011. Deenergization ,of cr4 by operation ofthe tarry timer switch tr'l also deenergizes 229 and CR3, permitting spring 205 to restore the valve elements to the position shown in Figure 13 where the pressure conduit I84 is connected through 201 to the loader cylinder, causing upward movement of plunger or slide I02 to work discharging position as shown in Figure 8. As this takes place, LS2 is released and opened while LSI is eventually closed and in the event that cycle selector switch 23l is in closed,

position will reinitiate succeeding cyclic opera-.

tion.

Attention is invited to the fact that, while for clarity of diagrammatic understanding of the operation, the elements LSI and LS2 have been shown as disposed respectively above and below the plunger actuating arm 21!, in the actual machine structure, as indicated in Figure 3, these switches are disposed on opposite sides of the chamber I05, the plunger pin 232 being contacted by the slide in its upward movement for actuation of LSI and a corresponding plunger 233 being coupled with LS2 having a head 234 directly engaged by the arm or flange 2 to exert a downward pull rather than direct push against the switch actuating arm, the principle of operation, however, being identical in the two instances.

From the foregoing description it will be evident that there has been provided an improved precision grinding machine in which by 'employment of a multiplicity of fine adjustments the work holding elements may be most accurately located with respect to a prospective grinding po-- sition. Furthermore, that there has been provided an improved manner of grinding wheel mounting and hydraulic control for successive rapid advance and controlled oscillatory'feed movements of the grinding wheel with respect to the predetermined preset work position, for definitely limiting the extent of movement of the grinding wheel, maintaining same for a desired period of time in firmly locked position, not subject to the creep or inaccuracy potentially inherent in ordinary slide and adjusting mechanisms.

vIt will further be noted that there has been provided an improved control mechanism for a grinding machine of this character which will insure the proper rapid continuous cyclic presentation of work pieces in self-stabilized position for grinding within the machine, for effecting the seou ntial movements of the work presenting and holding mechanisms, and the sequence of operative movements of the grinding wheel with respect thereto, together with automatic control mechanism for effecting interlocked, rapid and slow retracting movements of the grinding wheel, removal of a completed work piece and its replacement with a fresh work piece in continuous consequence.

What is claimed is:

1. An automatic grinding machine of the character described. including a work driving means and a work support means disposed adjacent thereto, a recipr'ocable work shifting device movable to deposit a work piece on the work supporting means, a work clamping element, means actuable by continued unidirectional movement of the work shifting means for efiecting the clamping of the work piece against the work driving means, a'work grinding element movable in a direction toward and from the work supporting means, means actuable by the said unidirectional movement of the work loading means for efiecting sequential rapid and feeding movements of the grinding wheel in the direction of the work supporting means for operation on a workpiece carried thereby, means for limiting the extent of feeding movement of the grinding wheel, a time delayreverse for effecting subsequent retraction of the grinding wheel, and means actuable on retracting movement of the grinding wheel for efiecting a reverse shifting of the work loading means to retract and discharge a completed work piece.

2. In a grinding machine Qof the character described, the combination with a bed or support, of a grinding wheel carrier oscillatably mounted thereon, a trunnion remotely supported b the bed at one side of the grinding wheel, a table having a portion pivotally supported by the trunnion at one side of the grinding wheel, said table having a work supporting portion projecting to the opposite side of the grinding wheel, a work support carried by the projecting portion in opposition to the adjacent portion of the grinding wheel, and means carried by the bed and subtending the work support for determining the position of the table with respect to the bed.

wheel, means carried by the bed and subtending the work support for determining the position of the table with respect to the bed, and means for adjusting the supporting means to shift the table about its trunnion and variably position the work support with respect to the grinding wheel.

4. In a grinding machine of the character described, the combination with a bed or support, of a grinding wheel carrier oscillatably mounted thereon, a trunnion remotely supported by the bed at one side of the grinding wheel, a table having a portion pivotally supported by the trunnion at one side of the grinding wheel, said table having a work supportin portion projecting to the opposite side of the grinding wheel, a work support carried by the projecting portion in opposition to the adjacent portion of the grinding wheel, means carried by the bed and subtending the work support for determining the position of the table with respect to the bed, said table supporting means being in the form of rollers, and means to longitudinally adjust the table on the rollers to vary the separation between the work support and the grinding wheel.

5. In a grinding machine of the character described, the combination with a bed or support, of a grinding wheel carrier oscillatably mounted thereon, a trunnion remotely supported by the guano:

bed at one side of the grinding wheel, a table having a portion pivotally supported by the trunnion at one side of the grinding wheel, said table-having a work supporting portion projecting to the opposite side of the grinding wheel, a work support carried by the projecting portion in opposition to the adjacent portion of the grinding wheel, means carried by the bed and subtending the work support for determining the position of the table with respect to the bed, said supporting means including a transverse, shaft having eccentrics thereon, supporting rollers journaled on the-eccentrics and in engagement with the table whereby rotation of the shaft will vary the elevation of the rollers and thus the I angular relationship between the bed and table,

and means for longitudinally adjusting the table with respect to the bed to vary the separation between the work support and grinding wheel, whereby the rollers will provide anti-friction supports facilitating said longitudinal adjustment of the table. j

v 6. In a grinding machin of the character deincluding a small diameter piston associated with scribed; the combination with a bed or support, I

of a grinding wheel carrier oscillatably mounted thereon, a trunnion remotely supported by the bed at one side of the grinding wheel a table having -a portion pivotally supported by the trunnion at one side of the grinding wheel, said table having a work supporting portion projecting to the opposite side of. the grinding wheel, a work support carried by the projecting portion in opposition to the adjacent portion of the grinding wheel, means carried by the bed and subtending the work support for determining the position of the table with respect to the bed, said supporting means including a transverse shaft having eccentrics thereon, supporting rollers journaled on the eccentrics and in engagement with th table whereby rotation of the shaft will vary the elevaship between the bed and table, means for longitudinally adjusting the table with respect to the bed to vary the separation between the work support and grinding wheel, whereby the rollers will provide anti-friction supports facilitating said longitudinal adjustment of the table; said projecting portion of the table having a portion thereof formed to provide an arcuate guideway, a pivot carried by the table and disposed concentric with the guideway, means interconnecting the pivot and work support; and additional means on the work supportengaging the guideway for securing the work support in desired angularly adjusted position about the pivot with respect to the adjacent operative portion f the grinding wheel carried by the bed.

40 tion of therollers and thus the angular relation- '7. A grinding machine of the character de- I scribed, including a bed, a work support adjustably mounted thereon, a trunnion carried by the bed, a grinding wheel pivotally mounted on the trunnion for oscillation in a direction toward and from the work support, means for effecting a controlled rapid approach and subsequent feeding movement of the grinding wheel toward the work support including a power transmittin element, a hydraulic piston and cylinder mechanism including a small diameter piston associated with the oscillatable grinding wheel carriage and acting against the element whereby on hydraulic actuation thereof a rapid relative movement between carriage and power transmitting element will be effected, a second large diameter piston reacting against the power element for effecting joint movement of the element and first-men- 14 v I tioned piston, a hydraulic resistor for said movement, and means for variably determining thethe oscillatable grinding wheel carriage and acting against the element whereby on'hydraulic actuation thereof a rapid relatiye movement between carriageand power transmitting element Joint movement of the element and first-mentioned piston, a hydraulic resistor for said movement, means for variably, determining the volumetric reaction of a hydraulic medium as respects the large piston to determine the rate'ot feed imparted thereby, and meansifor variably limiting the amount of oscillatory "movement impartable to the carriag whereby additional movement of the large piston will be absorbed by will be eflected, a second large diameter piston I reacting against the power element for 'eflecting yielding of'the smaller piston and the-oscillatory in unyielding position for accurate sparking-out operations.

9. In an automatic grinding machine of the character described, including a work support and an opposed grinding wheel support, a grinding wheel carried thereby a loader mechanismfor positioning a work piece in the operativ position on the work support, means actuable by' the loader for clamping the work in. operative position, a first means for efiecting movement of the grinding wheel toward the work support, a second means for effecting corresponding feeding movement at a slower rate, means actuable by the continued movement of the work loading device for initiating operation of the first grinding wheel moving means, additional means actuable on movement of the grinding wheel into prescribed position for initiating actuation of the second grinding wheel moving means, means for positively limiting the extent of movement of the grinding wheel, and distinct means actuable by movement of the grinding wheel feeding means independent of the positioning of the grinding wheel for effecting a reversal of the tion thereof.

10. Inan automatic grinding machine of character described, including a work support and an opposed grinding wheel support, a grinding wheel carried thereby a loader mechanism for positioning a work piece in the operative position on the work support, means actuable by the power actua-' the grinding wheel-carriage will be positively locked loader for clamping the work in operative position, a first means for effecting movement of the grinding wheel toward the work support, a sec- 0nd means for efiecting corresponding feeding movement at a slowen rate, means actuable by the continued movement of the work loading device for initiating operation of the first grinding wheel moving means, additional means actuable on movement of the grinding wheel into prescribed position for initiating actuation of the second grinding wheel moving means, means for positively limiting the extent of movement of the grinding wheel, distinct means actuable by movement of th grinding wheel feeding means independent of the positioning of the grinding wheel for efiectlng a reversal of the power actuation thereof, and means independent of the reversal controlling mechanism for variably determining the limit of power movement of the grinding wheel in a feeding direction.

11. In an automatic grinding machine of the character described, including a work support and an opposed grinding wheel support, a grinding wheel carried thereby a loader mechanism for positioning a work piece in the operative position on the work support, means actuable by the loader for clamping the work in operative position, a first means for effecting movement of the grinding wheel toward the work support, "a second means for efiecting corresponding feeding movement at a slower rate, means actuable by the continued movement of the work loading device for initiating operation of the first grinding wheel moving means, additional means actuable on movement of the grinding wheel into prescribed position for initiating actuation of the second grinding wheel moving means, means for positively limiting the extent of movement of the grinding wheel, distinct means actuable by movement of the grinding wheel feeding means independent of the positioning of the grinding wheel for effecting a reversal of the power actuation thereof, means operable on reversal of grinding wheel movement for effecting a subsequent reversal lOf movement of the work feeding mechanism, and a cycle control mechanism actuable on retraction of the work feeding mechanism for initiating the subsequent cyclic operation of the parts.

12. A mechanism of the'character described, including a bed or support, a trunnion carried thereby, a grinding wheel carriage pivotally mounted on the trunnion and having its mass disposedto one side of the trunnion, an operating lever pivoted to the bed and having a plurality of angularly related abutment arms, a first hydraulic motor having an abutment rod engaging one of the arms for actuation of the lever inone direction about its pivotal support, said first hydraulic motor being carried by the grinding wheel carriage and having its abutment shiftable relative to said carriage, a second hydraulic motor carried by the bed and having a shiftable abutment portion reacting against the lever to oscillate the same about its pivot in a direction opp site to that of the first hydraulic motor, whereby actuation of the second motor will through the lever and first motor eiiect an augmented movement of the grinding wheel carriage, a source of hydraulic actuating medium, and a-controlvalve mechanism intervening the source and said hydraulic motors for eifecting sequential actuation of the respective motors.

13. A mechanism of the character described, including a bed or support, a trunnion carried thereby, a grinding wheel carriage pivotally mounted on the trunnion and having its mass disposed to one side of the trunnion, an operating lever pivoted to the bed and having a plurality of angularly related abutment arms, a first hydraulic motor having an abutment rod engaging one of the arms for actuation of the lever in one direction about its pivotal support, said first hydraulic motor being carried by the grinding wheel carriage and having its abutment shiftable relative to said carriage, a second hydraulic motor carried by the bed and having a shiitable abutment portion reacting against the lever to oscillate the same about its pivot in a direction opposite to that of the first hydraulic motor, whereby actuation of the second motor will through the lever and first motor effect an augmented movement of the grinding wheel car riage. a source of hydraulic actuating medium, a control valve mechanism intervening the source and said hydraulic motors for effecting sequential actuation ,of the respective motors, a third hydraulic motor reacting on the lever in opposition to the second hydraulic motor, and means for coupling hydraulic pressure to said third hydraulic motor to impart a continuous unidirectional urge to the lever.

14. A mechanism of the character described, including a bed or support, a trunnion carried thereby, a grinding wheel carriage pivotally mounted on the trunnion and having, its mass disposed to one side of the trunnion, an operating lever pivoted to the bed and having a plurality of angularly related abutment arms, a first hydraulic motor having an abutment rod engaging one of the arms for actuation of the lever .in one direction about its pivotal support, said first hydraulic motor being carried by the grinding wheel carriage and having its abutment shiftable relative to said carriage, a second hydraulic motor carried by the bed' and having a shiftable abutment portion reacting against the lever to oscillate the same about its pivot in a direction opposite to that of the first hydraulic motor, whereby actuation of the second motor will through the lever and first motor effect an augmented movement of the grinding wheel carriage, a source of hydraulic actuating medium, a control valve mechanism intervening the source and said hydraulic motors for eifecting sequential actuation of the respective motors, a third hydraulic motor reacting on the lever in opposition to the second hydraulic motor, and means for coupling hydraulic pressure to said third hydraulic motor to impart a continuous unidirectional urge to the lever, said three hydraulic motors being in the form of reciprocable pistons, the combined effective areas of the pistons of the first and third hydraulic motors being less than the effective area of the piston of the second hydraulic motor whereby when power is applied to the several motors the second hydraulic motor will control the direction of movement of the lever.

15. A mechanism of the'character described, including a bed or support, a trunnion carried thereby, a grinding wheel carriage pivotally mounted on the trunnion-and having its mass disposed to one side of the trunnion, an operating lever pivoted to the bed and having a plurality of angularly related abutment arms, a first hydraulic motor having an abutment rod engaging one of the arms for actuation of, the lever in one direction about its pivotal support, said first hydraulic motor being carried by the grind.

ing wheel carriage and having its abutment shiftable relative to said carriage, a second hydraulic motor carried by the bed and having a shiftable abutment portion reacting against the lever to oscillate the same about its pivot in a direction opposite to that of the first hydraulic motor, whereby actuation of the second motor will through the lever and first motor effect an au mented movement of the grinding wheel carriage, a source of hydraulic actuating medium, a control valve mechanism intervening the source and said 17 hydraulic motors for effecting sequential actuation of the respective motors; a third hydraulic second hydraulic motor, means for coupling hydraulic pressure to said third hydraulic motor to motor reacting onthe lever in opposition to the 1 impart a continuous unidirectional urge to the f lever, said three hydraulic motors being in theform of'recip'rocablepistons, the combined eflective areas of the pistons of the flrst'and third hydraulic motors being less than the eflective area of the piston of the second hydraulic motor whereby when power is applied to the several motors the second hydraulic motor will control the direction of movement of the lever, and means independent of the hydraulic motors for limiting the extent of movement of the grinding wheel carriage eflectable by said motors.

direction oi the teed slide. and means carried by piece, means for sequentially positioning a series I of work pieces in operative position, in the machine including a bracket adjacent the work supports, ,a feeding plunger reciprocably supported by the bracket and having a work piece receiving recess, oppositely angularly disposed loading and I discharge chutes carried by the bracket and 16.- In a machine of the character described:

the combination with a work driving member, of work positioning members disposed adjacent thereto for peripheral engagement with a work piece, means for sequentially positioning a series of, work pieces in operative position in the machine including a bracket adjacent the work supports, a feeding plunger reciprocably supported by the bracket and having a work piece receiving recess, oppositely angularly disposed loading and discharge chutes carried by the bracket and adapted to communicate with said recess, anjinclined terminal carrier portion subtending the recessand adaptedwhen in raised position to -ma.gazine whenthe slide is raised and the gate substantially coincide with the lower wall of the discharge magazine and when in depressed position to subtend the work position as defined by the work supports, said slide having an intermediate gate portion positioned to block on the discharge aperture of the feeding magazine when in raised position and to block off the discharge magazine when in position to release the'work I piece from the feeding magazine whereby the released work piece willrollover the gate onto the carrier as the slide is. lowered but may be discharged from the carrier to the discharge magazine when the slide is-raised and the gate. is in upper work piece restraining position.

17. In a machine or. the character described, the combination with a work driving member, of

work positioning members disposed adjacent" thereto for peripheral engagement with aiwork piece-means for sequentially positioning a series of work pieces in operative position in the machine including a bracket adjacent the work supports. a feeding plunger reciprocably supported by the bracket and having a work piece receiving recess, oppositely angularly disposed loading and discharge chutes carried by the bracket and adapted to communicate with said recess, an inclined terminal carrier portion subtending the recess and adapted when in raised position to substantially coincide with the lower wall of the discharge magazine and when in depressed position to subtend the work position as defined by the work supports, said slide having an intermediate gate portion positioned to block oh the discharge aperture of the feeding magazine when in raised position and to block 01! the discharge magazine when in position to release the work piece from the feeding magazine whereby the released work piece will roll over the gate onto the carrier as the slide is lowered but may be discharged from the carrier to the discharge magazine when the slide is raised and the gate is in upper work piece. restraining position, a spring plunger engageable with work piece in the feed adapted to communicate with said recess, an in-' clined terminal carrier portion subtendingthe recess and adapted when in raised position to substantially coincide with the lower wall of the discharge magazinegandiwhen in depressed posi-.

tion to subtend the work position as'defined by the work supports, said slide having an inter-- mediate gate portion positioned to block of! the discharge aperture of the feeding magazine when in raised position and to block of! the discharge released work piece will roll over the gate onto the carrier as theslide is lowered but may be discharged from. the carrier to' the discharge is in upper work piece restraining position, a work ment with a deposited work piece on the work supporting members, and a cam means on the slide positioned to react on the clamping element subsequent to deposit of the work piece on the supporting elementsby the carrier and to disengage th -clamp' on retraction of the. slideprior to reengagement oi the carrier with the work piece.

19; A grinding machine 0! the character described, including a bed ora support, a grinding wheel carriage mounted thereon, a work supporting table carried by the support, means for effecting adjustment of the table in a first transverse plane and in a second vertical plane as respects the grinding wheel,- a pivot stud carried by th table and adjustable therewith, an arcuate guideway formed on the table and in .concentric relation to the stud, a work supporting unit mounted on the table having a portion interengaged with the stud and a restraining member interengageable with the arcuate way, means for eiIecting a radial adjustment of the unit with respect to the stud and restraining member, a work driving means slide mounted on the work supporting unit, means for eifecting transverse adjustment of the slide with respect tothe unit, a work driver carried by the slide, a bracket mounted on the unit and-extending upward in proximity to the work driving member on the slide, work supporting elements mounted on the bracket and adjustable relative thereto for determining the positioning of a work-piece with respect to the driving unit, and means for effecting a bodily adjustment or thebracket and work supporting elements as respects the driving element on the slide,

7 20. In a machine of the character described, the combination with a bed having longitudinally extending guideways, of a table having vertical magazine for limiting movement, thereof in the ways interfltting with the ways o t e b a l9 trunnion carried by the bed intermediate the ways, a guide block oscillatably supported by the trunnion, said block having guide portions interengaged with the table, adjusting means carried by the bed at a point remote from the trunnion and engaging the table tor variably positioning.

the same about the trunnion} and means for effecting longitudinal movement of the table with lrespect to the bed along an angular path defined by said adjusting means and the trunnioned suporting block. p 21; In a machine of the character described, the combination with a bed having longitudinally extending guideways, of a table having vertical ways interfitting with the ways on the bed, a I trunnion carried by the bed-intermediate the ways, a guide block wcillatably supported by the trunnion, said block having guide portions inter! engaged with the table, adjusting means carried by the bed at a point remote from the trunnion and engaging the table for variably positioning the same about the trunnion, means for eflecting longitudinal movement of the table with respect to the bed along an angular path defined by said adjusting means and the trunnioned supporting block, a grinding wheel overlying an intermediate portion of the table, and work supporting means mounted on the table and extending upwardly into opposition to the grinding wheel whereby longitudinal movement of the table will eiiect adjustment of the work support in an angular direction as respects the opposed grinding wheel.- 22. A machine of the character described including a grinding wheel and opposed work rest means for supporting a workpiece during action thereon by the. grindingwheel, a fixed end stopadjacent the work rest means forlimiting the 20 for angularly adjusting the table with respect to the bed to vary the resultant angle of longitudinal translation of the table with respect to the grinding wheel support.

25. A grinding machine including a bed and a grinding wheel support carried by the bed, a table member translatably mounted on the bed, work supporting means carried by the table member for movement toward and from the grinding wheel support upon translation of the table, means for determining the longitudinal path of translation of the table, and additional means for angularly adjusting the table with. respect to the bed to vary the resultant angle of longitudinal translation of the table with respect to the grinding wheel support, said means for determining the longitudinal path of movement of the table 111 eluding vertical guideways formed on the bed and cooperating interiitting guideways formed on the underside of the table and interfitting with the ways on the bed.

26. A grinding machine including a bed and a grinding wheel support carried by the bed, a table member translatably mounted on the bed, work supporting means carried by thetable member for movement toward and from the grinding wheel support upon translation of the table, means for determining the longitudinal path of translation of the table, additional means for angularly adjusting the table with'respect to the bed to vary the resultant angle of longitudinal translation of the table with respect to the grindlongitudinal path of movement of the table ineluding vertical guidewaysiormed on the bed and cooperating interfltting guideways formed on the underside of the table and interfitting with the wayson the bed, and said means for determining the angular path of translation of the table with respect to the bed including atrunnioned support carried by the bed for one end of the table.

27. A grinding machine including a bed and a V grinding wheel support carried by the bed, a table eluding a'grinding wheel and opposed work rest means for supporting a work piece during action thereon by the grinding wheel, a .flxed end stop adjacent the work rest means for limiting the axial movement of a work piece during a grinding operation, a work loading device reciprocable a work piece in the direction of the end-stop, and

interengageable cam and cam follower means on the end clamp and work loading means for shifting the end clamp in direction to longitudinally move a work piece on the rest against the fixed I end stop during continued movement of the work loading means in a work depositing direction.

24.'-A grinding machine including a bed and a' n ing wheelsupport carried by the .bed,a.tab1e member. translatablymounted on the bed, work supporting means carried by the-table member for'movementjtoward and from the grinding member translatablymounted on the bed, work supporting means carried by thetable member for movement toward and from the grinding wheel support upon translation of the'table, means for. determining the longitudinal path of translation of the table, additional .mea-ns for angula'rly adjusting the. tablewith respect to the bed to vary theresultant angle of longitudinal trans'lation of the table with respect to the grinding wheel support, said means for determining. the longitudinal path of movement'of the table including vertical guideways formedon the bed and cooperating interfltting guideways formed on the underside of the table and interfltting' with the ways on the bed, said means for determining the angular path of translation of the table with'respect to the 'bed'including a'trunnioned support carried by the bed for one end of the table, and vertically adjustable supports carried by the bed and engaging a portion of the underside of the table remote from the trunnion support.

support upon translation of the table, means for determining the longitudinal path of translation of the table, additional means for angula'rly adlusting the table with respect to the bed to vary the resultant angleof longitudinal translation of the table with respect to the grinding wheel sup- 28. A grinding machine including a bed and a aavasea path of movement or the table including vertical guideways formed on the bed and cooperating interfitting guideways formed on the underside of the table and interfitting with the ways on the bed, said means for determining the angular path of translation of the table with respect to the bed including a trunnioned support carried by the bed for one end of the table, and vertically ad- 22 support at one rate. a second hydraulic motor for effecting corresponding directional movement of the grinding wheel support at a slower rate, valve means far controlling the coupling of the actuating medium with the first motor, valve means for coupling ,the actuating medium with the second motor, means actuable by movement of the loader mechanim for shifting the valve to initiate operation of the first hydraulic motor,

justable supports carried by thebed and engaging additional means actuable on movement of the aportion of the underside of the table-remote j grinding wheel support into prescribed position from the trunnion support, said adjustable supfor initiating actuation of the valve for coupling portsincluding rollers facilitating longitudinal the hydraulic actuating medium to the second translation of the table. motor, means for positively limitingthe extent 29. A grinding machine including a bed and of movement of the grinding wheel support, sepaa grinding wheel support carried by the bed, a table member translatably mounted on the bed, work supporting means. carried by the table member for movement toward and from the grinding wheel support upon translation or the table, means for determining the longitudinal path of translation of the table, additionabmeans i'or angularly adjusting the table with respect to the bed to vary the resultant angle of longitudinal translation of the table with respect to the grinding wheel support, said means for determining the longitudinal path or movement or the table including vertical guideways formed on the bed and cooperating interfitting guideways formed on the underside of the table and interfitting with the ways on the bed, said means for determining the angular path of translation of the table with respect to the bed including a trunnioned support carried by the bed for one end or the table, and adjusting means --intervening the table and the trunnioned support for eflecting longitudinal translation of the'table in any angularly adjustable position thereof.

30.- A machine of the character. described, in-

, ratemeans actuable by," movement of the.grind-.

ing wheel support independent of its position for effecting a reversal of the power actuation thereof, and means independent ofethe reversal controlling mechanism for variably determining limit 4 e or power movement of the grinding wheel support 7 in a feed direction;

32. In a grinding machine or the character described, a work support and an opposed grind- 5 ing wheel supportya loader mechanism for posithe work support, a valve for controlling the coupling of the hydraulic mediumto said motor,

a solenoid control for the valve, an electric trip 1 mechanism having aportion disposed in the path of the loading device. whereby movement of the'loading device will actuate the trip mechanism to effect solenoid determined positioning of the valve to couple the actuating medium with the first hydraulic-motor, a second hydraulic motorifor'. effecting continued movement of thelu a bed, a work suppo an 8- 91 956 1 40 grinding wheel support, a-control valve forcougrinding wheel support carried by thei'bed; a loader mechanism for positioning'a work 1 piecel in operative position on the .work'fsupport', means;

actuable by the loader mechanism for clamping...

the work inoperative positiomgaffirs't hydraulic motor for effecting movementg'lof' itheijgrindingwheel in the direction of '-,the*cla'mped.-workrl piece, an electric control operableby'movement a second hydraulic motor for :efiecting addi j tional movement ofthe" grinding'wheel inthe direction ofthe work, an electric control ior said second'hydraulic motor,- a.-source,of,-hy-

control and initiate movement'oi the second hydraulic'motor', positive mechanical stop means for limiting'the movement of the grindin wheel in a direction or. the work support, electrical stop means activated by movement of the grinding wheelin the direction of the work support, and means to disconnect the power source from the motors when the electrical stop means are actuated. 1

31. In a grinding machine of the character described including a work support and an opposed grinding wheel support,'a loader mechanism for positioning a work piece in operative I .70 other by the movable support, means for rigidly position on the work support, work clamping means, cam means actuable by. movement of the loader to move'the clamp into workj'eng'aging position, a source of hydraulic actuating medium, a first hydraulic motor for effecting movement pling hydi'aulic'me'dium to said ,motor,-,a. sole .1 I noid1 'for determining the operative."position,-.oi said-second valve, an electrical tripj. device or determinin'githef activation of the solenoid,'i.said Y 'device including} a 'trip portion engageable .;by

the -grindingi wheelsupport) when the I latter is actuatedzby-the first motor to trip the control I g I for movement of the valve to energize the second of the loader for activating said hydraulicmotor,

'port ir'i'a direction toward the work support, a I

tarry trip actuable by movement or the grinding wheelsupportfand connectionsbetweenthe tarry trip andthe valve controlling solenoids to efiect. shifting of the valves to disconnect the hydraulic actuating medium from said first and second grinding. wheel support actuating hydraulic motors.

33. In a grinding machine, the combination 60 with a bed, of a work support carried thereby,

a grinding wheel supported by the bed, means for eflectlng relative approach and retracting movement of the parts including a movable member mounting one of said elements, a hydraulic motor for effecting movement of the element with respect to the bed, and means for determining the extent of such movement including interengaging abutment members, one of such abutment members being carried by the bed and the mounting one' of said abutment members on its supporting-element, the other abutment member including a sliding member having an L-shaped portion interlocking with the fixed abutment,

of the grinding wheel support toward the work screw means for effecting longitudinal sliding movement of the abutment, said abutment hav- 24 REFERENCES CITED The foilowingreferences are of record in the file of this patent:

UNITED STATES PATENTS Number Name Date Booth July 28, 1931 Harrison et a1. Jan. 5, 1932 Booth -1 Mar. 1, 1932 Romaine Apr. 9, 1935 Strong Oct. 28, 19%1 Price et a1. M21119, 19 13

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