US2101644A - Grinding machine - Google Patents

Description

`De.v7,'1937. HERNSTETAL 2101,644

' GRINDING MACHINE v Filed spt'. 10, 1935' I e Smeets-snee*L 1 Izq 7 f ooo WMATTORNEYA Dec. 7 1937. H ERNST 'Er AL 2,101,644

GRINDING MACHINE Filed sept. 1o, 1955 6 Sheets-Sheet 2 WWMWMATTORNEY.

Dec. 7, 1937. H.1= RNST Er AL GRINDING lvxAcHINE Filed Sept. 10, 1935 6 Sheets-Sheet 3 lig.' 5

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Dec, 7, 1937. H. ERNST Er AL GRINDING MACHINE Filed Sept. lO, 1935 6 Sheets-Sheet 4 w NMNI l ATTORNEY.

Dec.7, 1937. H ERNST ETA'L 2,101,644

GRINDING MACHINE Dec. 7, 1937. H ERNST E1- AL 2,101,644

`GRINDING MACHINE Filed Sept. 10, 1955 6 Sheets-Sheet 6 is 'E Patented Dec. 7,1937' j v' UNITED STATES 101,644 PATENT*l oFFlcE GRINDING MACHINE I charles .narici-th, ana Lester F.

Nenninger, Cincinnati, Ohio, assignors to'Cincinnati Grinders Incorporated, Cincinnati, Ohio, a 4corporation of Ohio 'T ApplicationSeptember 10, 1935, Serial No. 39,951

the production of cylindrical surfaces.

One of the principal objects of the present invention is the provision of an improved type of grinding machine which may be readily utilizedand employed for the performance of differing types of grinding operations, both those in which relative traversing of the work and tool are to be effected, and those in which movements only lof the work and tool toward and from each other are utilized in presentation of the work surfaces one to theother andinwhich the several movements may be either manually or automatically ected as desired. l'

A further object of the present invention is the provision of a machine for the purposes specified in which the physical effort on the part of the voperator in connection with manual control or eifecting of the several movements of the ma.-

chine as distinguished from their automatic operation will be minimized and at' the same time the accuracy of the adjustments in question under manual control will be facilitated.

A further object of the present invention is the provision o fa machine tool--as of the type hereinabove set forth for example-in which a single v .source of actuating power may be utilized for tive determination of the nature of cycle or extent of movement of any individual element controllable by the circuit as an entirety.

A further object of the present invention is the provision in connection Vwith a machine ofthis nature of an improved relationship ofl elements and controls therefor, whereby the same may be utilized alternatively for` the performance of a grinding operation of constantly controlled amount in the performance of certain operations on a `work piece or alternatively utilized for positioning purposes only when other operations are to Vbe performed. i

Other' objects and advantages of the present invention may be readily apparent by reference to the following specication considered in conjunction with the accompanying drawings illustrative of one embodiment thereof, but it will be Aunderstood thatany modifications may be made in the specific structural details thereof within A the scope of the appended claims without depart-V ing from` or exceeding the spirit of the invention.

Figure 1 is a front elevation of a grinding machine constructed in accordance With and embodying the principles of the present invention. Figure 2 is a fragmentary sectional view through a portion of the manually actuable table traverse control mechanism as on the line 2-2 of Figure 1.

Figure 3 is a` view partially in elevation and partially in section as on the lline 3-3 of Figure 1, particularly illustrating the several mechanisms for determination of the in and out position of the saddle of the machine. 'l

Figure 4 is an end elevation of the machine.

Figure 5 is a fragmentary sectional view as on the line 5--5 of Figure 1 showing the detailed construction of the reversing valve for automatic table cycle.

Figure 6 is a horizontal plan view partly in section, illustrating the mounting of and means for in and out adjustment of the saddle unit and the relationship of the Vvarious control devices carried by that unit.

Figure 7 is a fragmentary longitudinal sectional view particularly illustrating the guiding ways for the saddle and the means for effecting translation or reciprocation of the table with respect to the saddle.

Figure 8 is a fragmentary sectional View as on the line 8 8 of'Figure 6 illustrating certain details of the directional control member for the Y machine and the immediate adjacent manual table control mechanism.

Figure 9 is a section. at right angles to Figure 8 as on the line 9-9 of Figure 8-showing the detail` of the pilot valve and its portings.

Figure 10 is a fragmentary sectional View as on the line Ill- I0 of Figure l `showing the structure lof the rate control valve.

Figure 11 is a fragmentary sectional view as on line Il--Il of Figure 1 Ashowing the details of the selector valve.

Figure 12 is a similar section on line l2l2 of Figure 1 illustrating stop valve.

Figure 13 is a fragmentary sectional view as the'detailed features of the on the line l3-I3 of'Figyre 6 particularly illusy ltrating the pick-feed mechanism. Figure 14 is a fragmentary section through th pick feed actuatingv cylinder.

Figure 15 is a similar section of the-spring ac- Figure 1"! is a schematic diagram illustrating the complete hydraulic or fluid circuits of the` ways 2l supporting a saddle 22 toward and fromv the front or operators station as respects the machine.

Disposed at and rising `from the rear portion of the bed 20 is the column 23 supporting the spindle 24 of rotary grinding wheel 25, suitably driven as from motor 29. Rollers 21, carried by the saddle, cooperate with the ways 2l for facilitating the free movement of this member, the work and their heavy associated parts. The alignment of the saddle during this movement is in part maintained by the interfitting of the V ways 28 of the bed with corresponding ways 29 on the saddle. These latter are spacedand provide a recess to receive a screw 30, which at its rear end is interengaged withtheV nut 3i carried by the bed 2|] whereby rotation of the screw in one direction or another will cause a corresponding axial movement thereof.

As particularly illustrated in Figure 3, andat the left hand side of the diagrammatic view, Figure 17, the screw has a reduced forwardlyextending portion 32 providing a piston rod receiving the piston 33, movable in cylinder 34 which is carried by the saddle. on the rod facilitate free rotation f the screw 30 irrespective of existing pressure conditions vin the cylinder 34. It will thus be seen that by rotation of the screw an in and out, or forward and back', motion will be imparted to piston 33, and thus a push or pull exerted against the saddle 22, tending to move it either in or out as thev case may be. In addition, by introduction of an actuating medium in one end or the other of the cylinder 34 a. reactance will be effected between the cylinder end and the piston, causing a movement to be imparted to the saddle with respect to the screw and limited only by the stroke of the piston within the cylinder.

For eiecting rotation of the screw suitable mechanical power transmitting devices may be employed, such as the sleeve 35, splined intermediately on the forward portion'of the screw and having the gear and pinion connection as at 36 and intermediate'planetary gearing 31 with the ratchet wheel 38 disposed on the front of 'l the machine and operable as by pawl 39 on arm 40. Through this chain of gearing as the arm 40 is oscillated by link 4I and rock arm 42, for example, a pick feed effect is secured, gradually advancing the member 38 one or more teeth at a. time as preselected. From this movement minute increments of rotative' adjustment of the screw 30 are effected. More rapid adjustments may be effected by rotation of the member 38 as an entirety through the medium of handle 43, or fine adjustments by withdrawal of the pin 44 in the handle and utilization of the planetary gearing 45, this being a type of grinding wheel Anti-friction bearings v feed screw adjustment familiar to the art and, it is believed, not requiring further detailed illustratlon as in itself the particular manner of effecting adjustment of screw 30 forms no part of the present invention.

The adjustment effected or eifectible and the purposes of the piston and cylinder arrangement above referred to will be described in detail in connection with the general functionings of the hydraulic circuit and controls.

The saddle 22 is provided on its upper surface with the transversely extending ways 46 for the table 41, bearing the tailstock 48 and headstock 49 with its driving motor 50. Disposed in a suitably formed recess 5I in the saddle is the cylinder 52 secured to the underside of the table containing a piston 53 mounted on the hollow piston rod 54 having its ends secured to brackets 55 carried by the saddle. 'I'his hollow rod terminates adjacent the piston in outlets 56 and 51 for introduction of pressure between the piston and one or the other ends of the cylinder whereby the table is actuated longitudinally in a direction transversely of the saddle under control of the hydraulic pressure thus introduced.

Carried as by the T slot 58 at the forward edge of the table are the adjustable dogs 59 for engagement with the Wings or lugs 60 of the rotary plunger 6| coupled at 62 ywith a pilot valve 63, shown in detail in Figure 9, for effecting reciprocation of this valve. A handle 64 on the plunger facilitates this manual oscillation when desired. This plunger is mounted for vertical sliding movement against the action of spring 65, whereby the lug 60 may be shifted out of the path of their respective dogs when it is desired that the dogs shall, for any reason, be ineffective.

It is believed from the foregoing that the general mechanical structural features of the machine here in question should be clear.

We will, therefore, refer briefly, and particularly in connection with Figure 1, to the sequence of control devices appearing at the front or operators station as respects the machine as showing their actual relationship-they being correspondingly indicated but differently positioned in the hydraulic diagram illustrative of their operative effects in the interest of simpliflcation of the diagrammatic showing of the various hydraulic circuit couplings effectible thereby.

These controls, considered from left to right, include the panel A for the several electrical control switches, the hand wheel B,for determining the functioning of the hydro-mechanical manual table traverse controlling mechanism C; and the pilot and plunger valve unit D. Immediately following these is the screw adjusting unit E, the hydraulic infeed control mechanism F, the selector G and the automatic pick feed device 42. Subsequent to the member 42 are the starting and stopping unit H, the rate determining valve J and the reversing valve with tarry control at K.

The operation of the machine For an understanding of this, reference is made particularly to the diagrammatic view, Figure 17. As will there be noted, the circulation of the hydraulic actuating medium for operation of the machine is effected by a'pump 6B delivering the fluid from the diagrammatically indicated reservoir 61 and creating inline 68 a pressure, depending on the setting of the relief valve 69. Considering the several elements in the position settings are indicated in Figure 17, it will be -noted that line 68 has the branch 68A extending v 'to the starting Vand stopping valve H and the branch 68E extending to the rate valve JL Extending from the two ends of the table piston rod are the conduits 'lll and H which respectively terminate at the starting valve H. In the present instance, conduit 'l0 is coupled by H with conduit 10A, extending to the hydraulic follow-up valve mechanism forming a part of the unit C. Similarly, conduit 1l is coupled by H with HA also leading to unit C. Spanning the termini of conduits 10A and HA are the termini of a U- v shaped conduit 12 having a portion- 12A illustrated as extending to the top and down the right hand side of Figure 17, at all times forming an outlet-exhaust or reservoir connection, irrespective of any valve adjustments. A short conduit 13 has a pair of branch conduits 13A centrally disposed or intermediate conduits 'MA and TIA. This conduit 13 extends to ,the stop valve and in the vposition shown is coucillatablelvalve shifting arm C-t. The actual structural arrangement of these-parts will be receiving pressure from the several conduit memf probably best understood by reference to Figures 2 and 8, although the operation itself is probably more clearly brought out by the semi-structural diagrammatic view. Itis to be noted that the block 5, which forms the terminus for the several conduits is in the nature of an enlargement overhead, having a sleeve portion rotatably journaled in the saddle 22 and having grooves bers. This block is circumterentially provided with a gear portion C-- rotatable from handle B through themedium of the pinion B--i forming a driving train to the gear. ,v

Carried by the table as indicated in Figure -7, is the tape 'I'. This tape runs during the table movement immediaely over'roller C-l on the rotary stem C-, which carries the rock arm C-t. 'I'he pressure introduced from 68A into conduit 73 operates to move the piston C--B to the left, as viewed in Figure 17, shifting bell crank C-iil so that roller C-ii urges the tape T into engagement withroller C i. As a result, when the parts are so interengaged any movement of thertable will ,cause a correspondingv rotation of vmember Cet. From the foregoing, the operation of these parts should be readilyunderstood, and it will be seen that on vrotation of wheel B a rocking movement in one direction or the other will be imparted to block C+5 of member C. The table at this time, being stationary, and the arm C--t being thus held by the tape T from corresponding rotation, willl remain xed with the result that there will be a displacement in one directionor the other of the valve C-l, serving to couple one or the other y of ports 13A with either line 10A or THA, and at the same time coupling the other of these two lines with one or the other branch of exhaust line 12. This coupling connection means. that pressure will then be introduced into one or the other end of the table cylinder, while the opposite end is coupled with exhaust, tending to create a movement ofthe table stictlyunder manual control but in which no manual effort is required other than that for the slight oscillation of the controlling wheel B since the actual power for movement is supplied entirely by the hydraulic f system. Immediately the table starts to move, however, it will, through the tape, rotate the member C-B in a direction corresponding to that in which the member C- had previously been oscillated, therefore tending to shut oi the inlet and exhaust connections to the table cylinder and stopping its movement. From the foregoing it should, therefore, be readily apparent that a follow-up hydraulic power actuation of thetable has been provided in which both the direction, rate and extent of the movement of. the table .within the capacity of the hydraulic system are dependent entirely on the rate and direction of movement of the hand wheel B. It

will be noted that this adjustment can be utilized .either merely for positioning purposes or for actual traverse ofthe work during grinding if desired Following through linev 63A it will be noted that conduit 68B extends by way of valves F-t, conduit 63C, valve F-2, conduit 68D and selector valve G to conduit ttG, having a branch WF under pressure condition there shown urging piston S to close headstock motor control switch S' against the action of the spring pressed plunger S-t. A second branch tM extends to the' terminus of plunger valve V to shift it into an open position permitting ilow of coolant through linelt and discharged onto the work being ground.

' Automatic table recipocation..

This is edected by outwardly shifting valve H or toward the lower part of the shift as viewed in Figure 17. This movement serves in the iirst instance to disconnect conduit 'l0 from Hilti and instead couples'same with conduit 10B. Simultaneously, conduit 'H is disconnected from 'HA with the branch of exhaust conduit WA. This means that 13A and 'l2 are now both exhaust or non-pressure lines while the table cylinder communication lines havebeen entirely disassociated `with. the manual control unit and the clamping of the table moved tape T to the roll C-'i has also been released. The hydraulic actuating medium under pressure will now iiow,through conduit 63E and past the variably restricted orifice provided by the tapered portion of valve member` J-i, whose position in the rate valve J is'deter- 7 mined by the adjustingscrew J-Z and knurled operating knob J- 3. The now of medium will then proceed through chamber VJ-t and past the restriction imparted by the taper portion of the second valve member J- into conduit 68N, the

series 63 still continuing to be'the conduit through which pressure or actuating medium ows. The

reverse'valve K, as lindicated in the drawings, in y its intermediate position to bringout the fact that upon shifting of the lpilot to eiect 'a reversal of the `table movement there. is a slowing down or retardance a predetermined vamount both in the movement of the valve toits blocking position and its continued movement to reverse position; these effects insuring a suitable retardance oi' table movement as it approaches the prescribed end of its stroke and subsequent gradual acceleration, thus eliminating chatter or other deleterious conditions on the work piece set up by a roughv or sharp reversal. It will be apparent that `and coupled with HB and conduit 13 is discon-Q` nected from pressure conduit 68A and coupled' if the reverse valve is in its upper limit of movement the pressure from 68N will be coupled with 'I IB, thus tending to actuate the table toward the left in Figure 17 and coupling line 10B with branch of the exhaust conduitlZA. An opposite position of the reversing valve will, of course, reverse these effects and couple 68N with 10B, actuating the table toward the right.

The position of the reversing valve is determined by the adjustment of the pilot valve member, which itself receives the actuating pilot pressure uid through conduit 68H, branching from 68B intermediate the valves H and F. This pilot valve D in the position shown in Figure 17 directs the ow of actuating medium through conduit 15A to the upper piston terminus of the reversing valve for depressing same and at the same time directs the actuating iluid through conduit 15B to the right hand end of the pick. feed piston cylinder P, actuating this cylinder to the right and causing an oscillation of the trip arm P-I transmitted through shaft P-2 to rock arm 42. Spring plunger P-3 reacting on a second roel; arm P-4 serves to maintain member P-I in close engagement with the grooves of piston P and to retract the pick feed device as an entirety after the oscillatable feed increment has been transmitted by the picker pawl to the screw rotating mechanism.

When the pilot valve is depressed as respects the position shown in vFigure 17 it will, of course,

be obvious that if the pilot valve is shifted to itsI alternative position that 68H will then be coupled through 15C and the control port of rate valve J with conduit 15D while 15A and 15B will be simultaneously coupled with the discharge conduit as at 15E. This will cause movement of the reverse valve in the opposite direction and consequently a reversing in the direction of actuation of the table.

Particular attention is invited to the structural details shown at the lower portion of the reverse valve K in connection with the associat/eelements of the rate valve J, as ,these two together determine both the rate of automatic reciprocation and the rate, of tarry or delay between reciprocations and such slowing down effected as may occur at each end of the table movement. Their proper construction, therefore, insures smoothness of reciprocation without waste of grinding time.

As has been mentioned, member J-S serves to adjust valve J-l to variabiy restrict the flow of actuating pressure fiuid from 68E into chamber J-4. At the same time, through conduit J-G and associate cross passages the flow pressure is transmitted to the upper end of auxiliary valve piston J-5, tending to restrict the discharge of the actuating uid through 68N to the selected end of the table cylinder. It will thus be seen that these two valve portions cooperate in reducing or cutting down the flow in accordance with adjustment effected by rotation of screw J-2. At the same time, the other end of the taper valve portion J-I oppositely varies the resistance to dis- -charge of the pilot valve fluid through line 'I5-D f vided-it being understood that since whatever pilot valve uid is entrained in the cylinder portion at one end must reversely ilow through the pilot valve when the reversing valve is actuated in the opposite direction a restraint in the line to either terminus of the reversing valve is sufficient to correspondingly control its movements in both directions. When the reversing valve is in its extreme lower position, as viewed in Figure 17, or left hand position, as viewed in Figure 5, the initial flow or urge of the shifting fluid will strike the groove K--I and through axial cross ports be injected into the forward piston chamber. As this pressure starts an initial movement of the reversing valve, however, it will be noted that the groove K-I is shifted out of alignment with the exit port of conduit 15D. The actuating `fluid must then ow through the auxiliary port and series K-2 to enter or exhaust from this terminal chamber. 'I'he flow through passages K--Z is controlled as by a needle or throttle valve K-3 which may therefore be set to retard to any desired degree the rate of movement of the reversing valve through the intermediate stage of its positioning as indicated in Figure 17, and before it is in position to cause reverse movement of the table. It is further to be understood that, as indicated, the valve spool portions are preferably somewhat tapered so that the acceleration taking place will be a gradual one during an appreciable part of movement of the valve, which is a long stroke, in place of being effective subonly at the intermediateportion of the movement of the reversing valve and its iinal movement for reversal has started to be accelerated or removed from control of the tarry determining throttle K-i-3. This result can be accomplished by the provision of an auxiliary by-pass line for the pressure as at K-5 which will become effective to reintroduce the actuating fluid direct into K-l at a predetermined point in the stroke of the reversing valve so that it is only at the intermediate stage when 15D and K--I are both blanked by spool portions of the valve that the W of entrained actuating medium must be by way of the adjustable tarry device K-3.

In the modified form of reversing valve tarry control shown in Figure 18, the flow from '15D through the rate control valve serves to initiate movement ofthe reversing valve K, but as this is cut off, in place of the flow from 15D being directed through the tarry throttle K-3, a lead K-S is connected direct with the pressure line 68E flowing thence through the groove K-2 and i lead K--l to the groove K'-| in the valve, so that Manual control of saddle movement As shown in Figure 17 the start and stop valve H is connected by a. link L with the selector valve G in such manner that when the. valve H is shifted to couple the table selector lines with the unit C, the valve G is vsimultaneously shifted to couple conduits 68D and 68G. Alternatively, when the valve H is moved to couple the table cylinder with the automatic feed and reciprocation control valve G will be shifted through link -L then coupling pressure line 68K with ESG for causing flow of coolant and energization of the headstock motor. It is to be understood, however, that if preferred, the link L may be're- I l anche ber aligns with the lock-out pin R permitting` the pin to move downward into this recess and ithus disengage the notch F--3 of the flange F-t on the forward end of the rotary sleeve F-5 `which can be oscillated by manipulation of the lcontrol handle F-IU. By reference to Figure 1, it will be noted that the flange is provided with a pair of these notches so that the handle may be locked in either a raised or lowered position as desired. Slee've F-S is provided with the helical slot F-t receiving pin F-l on the valve F-2. Rotation of the sleeve in a clockwise direction from the positionshown in Figure 17 will cause an axial movement of the valve F-2 in a direction toward the rear of the machine. As illustrated, .this movement has been just sumcient to allow pressure from 68C to enter line 68D for actuation of the coolant and headstock pistons. A continued movement with concomitant shifting of the .yoke F-8 moves the fulcrum of the control lever M inwardly. Inasmuch as this lever has its left-hand end received in the shifter groove N formed on the stem of the saddle adjusting screw til, which screw is held against movement by its engagement with the nut 3|! on the bed, the rightv hand end of the lever will be swung inwardly, thus releasing the valve F-i which in turn will be inwardly urged by its spring F-9. The movement thus permitted of the valve F--l will operate to couple conduit t8--B containing the actuating medium under pressure `with conduit t@ extending to the forward end of the cylinder it for introducing pressure at this point against the piston da At the same time, conduit ti from the forward end ofthe cylinder is coupled by the valve with branch 'E2C of the exhaust conduit 112A. The pressure' introduced through conduit t@ will therefore tend to move the cylinder and thus the saddle toward the front of the machine. 'I'his action 'will reversely rock lever M-correspondingly reversely shifting `valve F-l to shut oli the introduction of pressure and thus discontinue themovement of the saddle. Itwill thus be seen that as the handle F-ill is moved downwardly, eecting an oscillation of the lever M in the one direction, that the reaction on' the valve F--i will cause a compensating movement of the saddle to reversely rock the lever until the stabilization point of the valves is reestablished. Consequently, both the rate and direction 0f movement of the saddle are directly controlled by and in proportion to the speed of movement of the lever F-it except as may be modified by the-tapering of the valve spools edecting reduced rate of shifting of the saddle as the valves reach their limit of stroke. 'It will further be noted that the exact effective relationship ofthe valves mi may be varied by adjustment of theabutment screw F-ii carried by t'ne lever so that, for ex ample, a suihcient movement of the valve F-l may be provided to uncover conduit ttD and initiate headstock and coolant actuation prior to i initiation of saddle movement. It is further to be understood that the direction of angularity of the groove F--5 may be reversed ifA desired, eecting merely a reversal of the nature of actuation as respects direction of lever movement so that downward movement of the lever will cause saddle.

an inward in place of outwar/d movementoi the The particular advantage of the foregoing coni trois should be readily apparent -to those conversant with the art in that it will be`seen that there has been here provided a structure utilizable either -ior a quick inland out positioning of the saddle as for removal and replacement of i work pieces, or inspection of work without any' change in the feed screw setting being used as the size determinant for the work, or which alter-- natively may be employed as for inieed grinding purposes with the relative movement of tool arid work directly under manual control of the operator. It is further to be noted that in either event the entire physical labor imposed upon the workman is that of moving the handle to rotate the member 11h-d, but that the entire power forv effecting the desired movement of the partsis supplied by the hydraulic system thus controlled. It is to be noted that for traverse grinding, the valve G is preferably so shifted that the pin R positively locks vmember F--t against oscillation so that the saddle is disposed-in either inwardly or outwardly adjusted position as preferredat one or the other limit of stroke of piston 33 within its cylinder, so that the pick feed or other adjustment of the screw alone may be used to in sure the proper accurate positioning of work and tool, and it is to this end that the optionally employable interlock L between. the automaticv traverse controlling valve H and the valve G have been provided. l Y

From the foregoing'descrijption considered in connection with the drawings, `the particularly novel andadvantageous features of our invention should be readilyapparent, and it will be noted that we have provided a structure in which all normally term"manual adjustmerlts of the machine, both as to relative in and out position of a tool and work and longitudinal vor traverse adjustments of these parts, while manually controllable, are'performed by the employment of power shifting devices, thus greatly relieving the cessive or alternative performance of these dierent types of operations while utilizing the same source of powerv` for edecting all desired movements. i

llt is to be understood in connection with the foregoing description of operation of the machine that a particular'cycle or relationship of movements as denitely illustrated has been set forth for purposes of presentation of a proper understanding of the invention and the structure by which the same `may be carried into eect." Attention is invited to the fact, however, that due to the independent settings 'or adjustments illustrated for most of the valve devices here employed or of the respective timing wherevsame are more or less interdependent, that dierent eiective cycles or varying sequence of reactions may be attained without in anywise departing from the a second hydraulic circuit alternatively. available for effecting corresponding movement of the parts, selector means for operatively coupling one or the other of said circuits with the parts to be shifted, settable means for predetermining the rate of movement to be effected by one of the circuits, and movable means included in the other circuit for effecting a rate of shifting of the parts proportionate to the rate of movement of said latter means.

2. A grinding machine including a grinding wheel and a work support, means mounting said parts formovement toward and from each other, a rst hydraulic circuit for actuation of said parts including hydraulically operated means for effecting alternate translatory and incremental feeding movements,v a second hydraulic circuit including individual servo-motor valve devices for determining respectively the translatory and the feeding movements, and means for selectively coupling either said hydraulically operated means or said devices with the shiftable parts and simultaneously disconnecting the other of said means or devices therefrom.

3. Means for effecting translation of the table of a grinding machine or the like, including a reversible hydraulic motor, a rst actuating circuit therefor including a rate determining member, a reversing valve, and means for shifting the "valve to effect reversal of the motor, a second hydraulic circuit including a reversing valve and a follow-up device for counteracting reverse positionings of the valve, a common source of hydraulic power for both of said circuits, and means for selectively coupling one or the other of said circuits with the reversible motor for determining the rate and extent of actuation thereof.

4. Means for effecting translation of the table -of a grinding machine or the like, including a vreversible hydraulic motor, a first actuating circuit therefor including a rate determining member, a reversing valve, means for shifting the valve to effect reversal of the motor, a second hydraulic circuit including a reversing valve and a follow-up device for counteracting reverse positionings of the valve, a common source o f hydraulic power for lboth of said circuits, means for selectively coupling one or the other of said circuits with the reversible motor for determining the rate and extent of actuation thereof, said follow-up device including a shiftable member, a member movable with the table, and means for operatively connecting the table member land shiftable member when the follow-up circuit is coupled with the motor.

5. In a machine of the character described, the combination with `a pair of relatively movable parts, of a piston and cylinder mechanism for effecting m vement of the parts, an hydraulic actuating niedium introducible into the cylinder for effecting movement of the parts, and a plurality of serially arranged control valves intervening the source of hydraulic power and the cylinder, means for effecting axial movement of one of said valves to vary impelling connection of the hydraulic medium, a lever fulcrumed to the axially movable valve and shiftable therewith, said lever having a portion interengaged with another of the serially disposed valves for eiecting a simultaneous movement of the second valve upon shifting of the first, and means operable on actuation of the piston and cylinder mechanism for oscillating the lever to reversely vary the relationship of the valves and discontinue the hydraulic actuation of the motor.

6. In a machine of the character described, the

combination with a pair of relatively movable' parts, of a piston and cylinder mechanism for effecting movement of the parts, an hydraulic actuating medium introducible into the cylinder for effecting movement of the parts, and a plurality of serially arranged control valves intervening the source of hydraulic power and the cylinder, means for effecting axial movement of one,of said valves to vary impelling connection of the hydraulic medium, a lever fulcrumed to the axially movable valve and shiftable therewith, said lever having a' portion interengaged with another of the serially disposed valves for effecting a simultaneous movement of the second valve upon shifting of the first, means operable on actuation of the piston and cylinder mechanism for oscillating the lever to reversely vary the relationship ofthe valves and discontinue the hydraulic actuation of the motor, an additional valve serially arranged in the hydraulic circuit for determining certain of the operative effects thereof, and an interlock between the first and third valves preventing their simultaneous operation.

7. In a grinding machine of the character described, the combination with a grinding wheel and work support of means mounting said parts for relative translation, additional means mounting said parts for relative feeding movement, a first hydraulic circuit including rate and direction determining valves and a feed device, means jointly controlling the operation of the direction determining and feeding devices, a second hydraulic circuit including a combined rate and direction determinator, and means for operatively connecting either the rst or the second hydraulic actuating circuit with Athe translatable member for determining the operation thereof.

8. In a grinding machine of the character described, the combination with a grinding Wheel and work support of means mounting said parts for relative translation, additional means mounting said parts for relative feeding movement, a first hydraulic circuit including rate and direction determining valves and a feed device, means jointly controlling the operation of the direction determining and feeding devices, a second hydraulic circuit including a combined rate and direction determinator, means for operatively connecting either the rst or the second hydraulic actuating circuit with'the translatable member -for determining the operation thereof, an additional feedng mechanism including an hydraulic operating circuit, and means selectively determining the operative connection of the rst or thirdfhydraulic circuits with the relatively shiftable units of the machine.

9. A mechanism for manual control of the rate of translation of a grinding machine table or the like including a, reversible hydraulic motor coupled with the table f or actuation thereof, an hydraulic actuating circuit including a source of hydraulic medium under pressure, a rotarily adjustable valve member continuously coupled with saidv source of pressure, 'means for 'operatively coupling said valve member with the hydraulic motor, a second valve member cooperating with 'the rst for determining the effective coupling therethrough of the power source to the motor, a member shiftable with the table,and means for automatically coupling said member to one of a V a l 2,101,e44 the rotatable valvedevices upon connection of the control unit with the table motonsubstantially as and for the purpose described.

10. `An hydraulically operable grinding machine including a grinding wheel and an opposed work supporting table, means for effecting relative translation and feeding movements of said members including a reversible hydraulic motor, in-

dividual to each of said movements, afirst hydraulic actuating circuit for one of the motors coupling of the iirst hydraulic circuit with one of the motors or the servo-motor devices with their respective motors whereby the machine may be selectively, automatically, or manually controlled.

11. In a machine lof the character described,

the combination with a bed,a grinding wheel and a work support mounted on the bed for movement toward and from each other, of means for controlling said movement including a nut, an adjusting screw telescoping therewith, means nontranslatably securing one of said two last named of hydraulic relative movement of the nut-screw members with respect to the movable parts carrying the hydraulic device is definitely manually contro1lable,-and means for locking the servomotor structure against operation substantially as and for the purpose described. 13. A machine of the character described, the combination with a `bed or support and an hydraulically actuable' slide mounted thereon, of a rst valve controlled circuit for effecting reciprocaton of the slide, a second alternatively employable 'circuit for eiecting reciprocation of the slide including a servo-control device, and means to simultaneously mechanically and hydraulically couple said device with the slide for determination of the actuation thereof.

14. A device of the character described, the combination with a bed or support and a slide member reciprocable thereon, of a hydraulic control circuit coupleable with the slide for actuation thereof, said circuit including a pair of relatively movable valve parts providing a servo-control therefor,asource of actuating medium, `and means for simultaneously hydraulically coupling said source of medium with said circuit and mechanically coupling one of said servo-control parts with i members to one of `the movable parts, an hy-v draulic motor including a piston and cylinder, meansl connecting one of said devices with' the 1 other of said relativelymovable parts'and the other of said devices with the other of said members whereby said hydraulic motor provides a n shiftable connection between one part ofthev nut shiftable members, a i'lrst means including a second hydraulic motor for effecting a unidirectional relative rotation of the nut and screw to eiect denite incremental adjustment ofthe parts, and asecond means including a servo-motor control A and screw mechanism and one of the `relatively hydraulic circuit for determining both the rate and direction of introduction oi hydraulic actuatingafmedium into the rst hydraulic motor for eiecting a shifting movement of the piston relative to the cylinder whereby the rate and extent J of hydraulic relative movement ofthe nut-screw members with respect to the movable part carrying the hydraulic device is definitely manuallycontrollable and means for selectively/,determini ing the operative connection or said vsecond mean with said rsthydraulic motor.

l2. In a machine of the character descrimd,v

, draulic m torincluding a piston and cylinder,

the movable slide, substantially as and for the purpose described.

15. A machine of the character described, the combination with a, translatable slide and a hydraulic motorl for effecting translation thereof, of a pair of alternatively employable hydraulic circuits for determining actuation of the motor, one of said circuits including a pair of relatively movable parts providing aservo-control, a selector device for determining the operative coupling of the respective circuits with the hydraulic motor, and means controlled by the selector device for mechanically connecting one of the parts to-the slide, substantially as and for the purpose described.

16. In a machine of the character described, the combination with a bed or support, the slide movable thereon, of a hydraulic motor for effecting movement of the slide, a control circuit for said hydraulic motor Vincluding a servo-device comprising a pair of rotors, means for eiecting rotary movement of one of said rotors', and means for detachably coupling the other rotor with the slide for actuation thereby on reciprocation of the slide.

17. A machine of the character described, the combination with a bed or support and a member slideable thereon, of means for effecting movement of the member including a hydraulic motor,

means connecting one of said devices with the other of said relatively movable parts and the other of said devices with the other of said mem-- bers whereby said hydraulic motor provides a shiftable connection between one part oi the nut and screw mechanism and one of the relatively shiftable members, a first means for edecting a relative rotation of the nut and screw to edect deiinite incremental adjustment of the parts, and a second means including a servo-motor control hydraulic circuit for determining the rate and direction of introduction 'or hydraulic actuating medium into the hydraulic'motor for eiiecting a shifting movement of the piston relative to the cylinder whereby the rate and extent f a source 'of hydraulic fluid for actuation thereof, andia control circuit for the motor including a servo-device having a pair of interrelated rotors,

means on the member coupleable with one of said rotors for edecting rotation thereof during translation of. the member, a hydraulic circuit intervening the pressure source and the actuating motor, and means for completing the circuit from said source to the motor by way of the servodevice and simultaneously positively coupling the rotor with the movable member for`actuation thereby.

18. A machine of the character described, in-

cluding a support and a member translatablev thereon, a hydraulic power source, a rst throttle controlled circuit intervening the power source and a movable member for eiecting shiftingl selector means shiftable to effect simultaneous mechanical and hydraulic coupling of the servodevice to the member.

19. A machine of the character described, including a bed or support, a table and a grinding wheel support mounted thereon, slides intervening said parts whereby relative traverse and approach and receding movements thereof may be eiected, hydraulic motors individual tov the respective slides for effecting said movements, a hydraulic control circuit for each of said motors, each of said circuits including/a servo-motor device for determining rate and direction of movement of its individually controlled motor in proportion to the extent of actuation of the device, and a single control device simultaneously effective hydraulically and mechanically to disassociate both of said servo-controls from their respective slides.

HANS ERNST. CHARLES HERFURTH. LESTER F. NENNINGER. l

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