US2313482A - Multiple wheel grinding machine - Google Patents

Description

March 9, 1943. H. N. ROCKS ET Al 2,313,482 7 MULTIPLE WHEEL GRINDING MACHINE Fi led June a, 1940 '7 Sheets-Sheet 1 Zslwcntors HUGH u. BocKs M/LBUBN n. HOLLENQREEN HAROLD EBALSIGEE 62 (itto rncg H. N. ROCKS ET AL 2,313,482

MULTIPLE WHEEL GRINDING MACHINE March 9, 1943.

Filed June 6, 1940 .7 Sheets-Sheet 2 March-9, 1943. H. N. ROCKS ET AL MULTIPLE WHEEL GRINDING MACHINE 7 Sheets-Sheet 5 Juventprs Huqu N- a e/(s MILBUBN A-HOLLENGIEEEN HAROLD E. .BflI-SIGER March 9, 1943..

Filed June 6, 1940 '7 Sheets-Sheet 5- m J m m a m m G IQ 1| T LG 5 Ymh m as .NE NW n L fim Hm \2 N64 MNx N4 March 9, 1943.

H. N. ROCKS ET AL MULTIPLE WHEEL GRINDING MACHINE Filed June 6, 1940 '7 Sheets-Sheet Inventors HUGIH N- ROCKS MILBURN A- MQLLENQR'EEN HAROLD E..BAL8IGE2 March 9, 1943.- H. N. ROCKS ET AL I 2,313,482

MULT IPLE WHEEL GRINDING MACHINE 4 Filed June 6, 1940 7 Sheets-Sheet '7 Inventors HUGH N. zocxs 5 MILBURN A. HOLLENGEEEN (Ittmeg Patented Mar. 9, 1943 MULTIPLE WHEEL GRINDING MACHINE Hugh N. Rocks, Milburn A. Hollengreen, and Harold E. Balsiger, Waynesboro, Pa., assignors to Landis Tool Company, Waynesboro, Pa.

Application June 6, 1940, Serial No. 339,192

24 Claims.

Our invention relates to metal working machines, particularly grinding machines of the type having a plurality of wheels on a spindle for grinding a plurality of axially aligned bearing surfaces simultaneously.

It is an object of our invention to provide a machine wherein the cycle of operations after loading is performed automatically.

A further object is to provide a loading mechanism for a machine of this type.

A further object is to provide means responsive to movement of said loading means for iniitating a predetermined cycle of operations.

A further object is to provide a machine wherein each operation in a cycle is initiated in response to a previous operation.

Our invention resides in the mechanisms for efiecting sequential operation of the various elements of the machine. The work piece is placed on a loading device which in turn is shifted to place the work in alignment with the head and footstock centers. Movement of the loading device into this position operates a switch which causes the footstock center to move axially to pick up the work and to shift same into operative engagement with the headstock center. At a predetermined point in this movement of the footstock a locating member is moved into position adjacent a flange on the work piece. In response to movement of said locator the work carriage is shifted to the right to cause said flange to approach said locator. When the work has been properly positioned the carriage stops, the locator is withdrawn, the grinding wheel is advanced toward the work, and the work rest is also moved into contact with the work. Movement of the work rest may occur simultaneously with advance of the wheel, or it may be delayed until after the wheel has started to grind depending upon the characteristics of the work to be ground, or it may be initiated manually at any time. The grinding operation may be controlled by any suitable sizing device or timing mechanism. When the work has been ground to size, the wheel base is withdrawn and the withdrawal movement is utilized to efiect withdrawal of the footstock center. The work piece thus released is lifted out of grinding position by the spring actuated loader. When the loader releases the normally closed switch which actuated the footstock, a solenoid valve is shifted which moves the carriage to the left, where it remains until another work piece is placed in position, when the above described cycle is repeated. Withdrawal of the footstock center and movement of the carriage to the left may be initiated simultaneously, also.

Figure l is an end elevation.

Figure 2 is a plan view.

Figure 3 is a sectional end view on line 3-3 of Figure 4 of the loading mechanism.

Figure 4 is a plan view of the loading mechanism.

Figure 5 is a plan view of the footstock partly in section.

Figure 6 is a partial plan view of the footstock.

Figure 7 is an end view of the locating device.

Figure 8 is a front elevation of said device.

Figure 9 is a front elevation of the locating device showing its relation to a work piece.

Figure 10 is a diagram of the hydraulic system.

Figure 11 is a wiring diagram.

In the drawings, numeral It] indicates the bed of a grinding machine, H a work carriage slidably mounted thereon, [2 a swivel table on said carriage, I3 a footstock on said swivel table, and M a headstock, also on said swivel table. A work piece [5, in this case a crankshaft, is rotatably supported on headstock center 16 and footstock center ll. Rotation of said crank is effected by a motor 18 driving the headstock spindle (not shown) thru suitable gearing or belt connections. A steady rest 19 supports the work against the action of the grinding wheel. A longitudinal movement of carriage H is effected by a hydraulic motor consisting of a cylinder 20 secured to the bed and a piston slidably mounted in said cylinder. A piston rod 22 on said piston is secured to a bracket 23 on carriage ll. Said movement may be efiected manually by handwheel 24 thru any suitable transmission. A wheel base is slidably mounted onbed IE) for transverse movement toward and from said work piece. A spindle (not shown) rotatably mounted in spaced bearings on said support carries one or more grinding wheels 31. A wheel dressing mechanism 32 is mounted on said support 30 behind said wheels. This mechanism is described in detail in co-pending application Serial No. 220,776 filed July 22, 1938. The mechanism for effecting said transverse movement is shown here only in diagrammatic form but is shown and described fully in co-pending application Serial No. 196,254 filed March 16, 1938, now Patent No. 2,211,530, granted August 13, 1940.

Loading mechanism The mechanism for placing the work in grinding position consists of a pair of end members 40 and 4| which form a base or support for the mechanism. A shaft 42 is rotatably mounted in said members near the bottom thereof. Said shaft forms a pivoted support for a pair of arms 43 and 44 secured at opposite ends thereof. A second shaft 45 joins said arms at another point. A pair of springs 43 and 41 are attached at one end to shaft 45 and at the other end thru links 48 and 49 to end members 40 and 4i respectively. Said springs serve to hold arms 43 and 44 in the position indicated at A.

A pair of arms 58 and 5| are secured to shaft 45. Said arms are urged in a counter-clockwise direction by springs 52 and 53 attached to one end of said arms. The other end of each of said arms is shaped to receive a work piece. A downwardly projecting portion of arm 5| engages an adjustable stop 54 in end member M which determines the extent of movement of the arms 50 and 5| toward the work supporting centers I6 and I7. Movement of arm 43 is limited by the adjustable stop 60 engaging lug 52 in the end member 4I. Similar elements, not shown, limit the movement of arm 44.

A dog 05 on arm 5I serves upon movement of the loader to place a work piece in grinding position to depress an arm 64 on shaft 6?. At the other end of said shaft is a second arm 68 adapted for operative engagement with a limit switch 68. The function of said switch is to initiate operation of the footstock to pick up the work piece and shift it against the headstock center. A red I supported in said end members 40 and 4i has a disk II mounted at the headstock end. A spring I3 on said rod urges said disk against nuts I4 on said rod. Said disk is so positioned that if moved far enough axially it will engage a flange on the Work piece and shift said piece off the headstock center. A means for so shifting said disk consists of the bracket I attached to said footstock center and extending into operative relation with said rod. Said bracket is movable relative to said rod but the movement is limited by adjusting nuts I6.

Footstoclc The footstock I 3 is of conventional construction consisting of a sliding sleeve 80 in one end of which is inserted a center I! and in the other end of which is adjustably mounted a piston rod BI. Piston 82 is mounted in a cylinder 83. A cap 84 on said cylinder retains a spring 85 which urges said piston and footstock center to the left. Said piston is shifted to the right by fluid under pressure from a valve 06 shown diagrammatically in Figure 10. Said valve may be actuated in one direction by a spring 81 and in the opposite direction by a solenoid B3.

Attached to cylinder 33 is astart and stop valve 90. A valve stem 9! passes thru one end of a bracket 92 which may be adjusted thereon by nuts 93. The other end of said bracket is attached to rod 94 slidably mounted in the foot stock base I3. Said rod may be shifted to the left by means of a lever 95. Said rod might also be shifted automatically in response to the operation of the wheel base or some other suitable mechanism. However, the function of this Valve is to initiate operation of a steady rest, to be described later. As the time for starting such an operation differs considerably from piece to piece, it is preferred to leave the control to the judgment of the operator. Means for shifting said valve in the opposite direction to withdraw the back rest consists of a fluid line 95 from the left end of cylinder 33 to the left end of said valve 90.

A switch I03 mounted on said footstock is adapted to be actuated by movement thereof. The means for actuating said switch consists of an arm I pivoted to one end of a shaft WI and having one end in contact with tailrod I02 on piston 82. Said shaft is mounted in a protruding portion E24 of a member I 25 forming part of cylinder 33. A lug its on said portion has at tached thereto one end of a spring I 01. The other end of said spring is attached to arm I00 and serves to hold said arm in contact with tailrod I02 as described above.

On the other end of shaft IfiI is secured an arm H6. A cam III at one end of said arm is pivotally supported thereon. Rotation of said cam in a counter-clockwise direction is limited by a positive stop (not shown), and in a clockwise direction it is limited yieldingly by a spring I I2. The function of said arm is to actuate said limit switch I03 in timed relation with the movement of the footstock. The limit switch in turn controls a work locating device.

LOCIZtOT A device for effecting longitudinal location of the work and wheel consists of a locating feeler I25 disposed in the path of travel of a flange or other portion of the work. Said locating feeler is pivctally supported on a member I2! which is in turn carried by two parallel arms I22 and I23 pivotally attached to a bracket I24 on wheel fender I25. Another arm I26 is attached to arm I23, and also to a piston rod I21. A piston I28 on said rod is slidably mounted in a cylinder I29. Said cylinder is in turn mounted on said fender I25. A two pole switch I38 is mounted on said fender in such a position as to be actuated by movement of arm I26. Said member I2I supports a dial indicator I3I and a limit switch I32. Said indicator and switch are actuated by arms I33 and IE4 respectively on locating feeler I20. Said locating feeler is yieldingly held against counter-clockwise movement by a spring I35,-one end of which rests against arm I33, the other against a portion of a lug I30 on member I2I. Clockwise movement due to said sprin is positively limited by a stop screw in lug I30 and disposed in the path of another lug I3! on locating feeler I25.

Feed mechanism The structure of the feed mechanism used on our machine is described in co-pending application Serial No. 196,254 filed March 16, 1938, now Patent No. 2,211,530, granted August 13, 1940. Briefly it consists of a piston I40 and a, cylinder I4l for shifting a feed screw and nut (not shown), aligned with the wheel support 30 toward and from working position. As the piston I40 moves the wheel support 30 toward working position the exhaust fluid from cylinder I4I may pass freely thru a normally open solenoid actuated valve I42, or if said valve is closed it must pass thru a throttle valve I43. The function of the throttle valve is to slow down the rapid feed movement suificiently to grind surfaces such as shoulders, crankcheeks, etc. The solenoid I 44 which actuates said valve is energized by a switch I45. Said switch may be held in inoperative position by some portion of the wheel support 30 or the mechanism for moving said support, in this case a tailrod I46 on the piston I40. Said switch may be adjusted in any suitable 'toward working position.

manner to function at any desired predetermined time during the rapid feed movement. A pressure switch I41 is connected into the line thru which fluid is directed to move the support 30 A second piston I50 is a cylinder II acts thru a rack and pinion or an equivalent mechanism (not shown) to rotate the feed screw or nut and thus efiect a slow feed movement of said wheel support. Fluid under pressure for actuating said piston during a grinding operation is controlled by solenoid valve I55. Said valve is actuated in one d rection by a solenoid I56 and in the opposite direction by spring I51. Solenoid I56 is energized by switch I58. Said switch is actuated by the tailrod I46. The relative position of sa d switches is such that switch I45 is released first and just as the wheel approaches the peripheral surface to be ground, switch I58 is released to start the grinding feed. Fluid under pressure for moving the piston I 40 in either direction and for resettin piston I50 is controlled by a reversing valve I60. Said valve may be actuated in one direction by a spring IEI and in the opposite direction by a solenoid I62.

Steady rest operating mechanism Steady rest I9 is similar to that shown and described in co-pending application Serial No. 274,439 filed May 18, 1939. ference is in the mechanism for efiecting intermittent rotation of the adjusting screws. Said mechanism, shown diagrammatically in Figure 10, consists of a valve body I in which are slidably mounted two hydraulically interlocked reversing valves HI and I12, one of which directs fluid under pressure intermittently to two hydraulic motors I13 and I14. Said motors are attached to the adjusting screws of steady rest I9. For the sake of convenience, start and stop valve 90 shown and described in connection with the footstock mechanism of Figure 5, is shown in Figure 10 as being mounted in valve body I10. Valve 90 has a passage 91 formed therein joining spaced radial passages 98 and 99. Said passages open into chambers I08 and I09 respectively. Fluid under pressure enters valve 99 thru chamber I09 and is directed by passages 99 and 01 to passage I80 in valve body I10 leading to valve I1I. Said passage I80 continues as thru valve I1I to supply fluid to valve I12. A pair of passages I8I and I82 lead from passage I00 to the ends of valve I12. Relief valves I83 and I84 in each of said passages determine the pressure in each passage independently. Valve I1I directs fluid from passage I80 thru one or the other of passages I85 or I85 to opposite ends of valve I12 to reciprocate said valve. Fluid supplied to valve I12 thru passage I80 is directed thru one or the other of passages I81 or I88 to opposite ends of valve I1I to reciprocate same. A throttle valve I89 in passage I08 determines the rate of movement of valve I H and thus the frequency of reciprocation of valve I12. Fluid supplied to valve I12 thru passages ISI and I82 is directed alternately thru passages I00 and ISI to fluid motors I13 and I14. Exhaust passages I92 and I93 have connections to each of the valves 90, HI and I12 for carrying on any exhaust fluid passing thru said valves. For resetting the steady rest, fluid under pressure is directed by valve 90 thru passage I15 which divides to carry fluid to both of the motors I13 and I14. Said motors are thus actuated in a The principal difpump motor 228.

direction to return the work engaging members to inoperative position.

Size control mechanism Size control may be efiected either by controlling the duration of the grinding operation or by the use of a caliper to indicate a change in size of a work piece.

The caliper type of size control is shown in 00-. pending application Serial No. 196,254 filed March 16, 1938, now Patent No. 2,211,530, granted August 13, 1940. In this application we make use of a conventional time control mechanism, which consists of a two pole normally closed relay 200, a cam 20I for actuating said relay, a motor 202 for driving said cam, a clutch 203 for connecting and disconnecting said cam and motor, and a solenoid 204 for actuating said clutch.

The motor 202 may be connected as soon as the rapid feed starts but the actuation of the clutch 203 is preferably delayed until the grinding feed begins and is therefore connected into the circuit with solenoid I50 and. switch I58.

Operation To start our machine, the operator closes start switch 2I0 which connects line I thru stop switch 2 with a series of thermal overload relays 2I2, one for each of a plurality of electric motors, and with a relay 220 to start pump motor 22I for driving the pump which supplies lubricant to the spindle for rotatably supporting the grinding wheels 3I.

When sufiicient pressure has been built up in the spindle lubricating system. pressure switch 222 completes a circuit from contact 223 of relay 220 to energize relay 225. Said relay 225 starts wheel motor 220, oil pump motor 221, and coolant Fluid under pressure for actuating the various mechanisms is supplied by a pump 229 thru a main conduit 231, and a number of branch conduits 231a, 2311), etc. A check valve 238 prevents a return of fluid thru pump 229 when said pump is stopped. A relief valve 239 described in detail in co-pending application Serial No. 321,310 filed February 28, 1940, compensates for variation in viscosity of the fluid. A throttle valve 244 in line 231 determines the pressure of fluid delivered to the hydraulic system.

Headstock motor I8 may be started manually by a jog switch 230 which completes a circuit from line i thru line 23I bypassing normally open pressure switch I41, thru line 232, normally closed 4 contact 233 of relay 234 to motor control relay 235, and then thru line 236 to line 3. The only result of closing switch 230 is to start the motor.

A work piece I5 is placed on arms 50 and 5| in a portion thereof formed to receive same. Said arms are then swung into alignment with-the centers I6 and I1. This movement is limited by stop 54 which locates arm 5|. As arm 5I engages stop 54 a dog 65 actuates arm 55 to release normally closed switch 68. Releasing said switch closes a circuit between lines 240 and 24I but the circuit is open to line I at the normally open contact 242 of relay 243. Releasing switch 68 opens a circuit thru the normally open contacts thereof between line I and the footstock solenoid 88 thus deenergizing said solenoid. Spring 81 then shifts valve 85 to connect fluid line 250 with exhaust line 260 thus permitting the escape of fluid from footstock cylinder 83. Spring 05 then shifts piston 02 and center I1 to the left to engage work piece I5. As footstock center I1 moves to the left, tailrod I02 releases arm I00, and spring I01 causes said arm along with shaft II, arm I I0, and cam III to move in a counter-clockwise position to actuate normally open limit switch I03. The time of actuation of said switch relative to the footstock movement may be adjusted by adjusting the position of arm I on shaft III! or any other suitable arrangement. We prefer to actuate said switch slightly before the end of the footstock movement which shifts the crank I5 onto headstock center I5. Closing switch I03 completes a circuit thru normally closed contact 255 of relay 255 to energize locator solenoid 23!. Said solenoid shifts valve 262 against spring 263 to direct fluid under pressure from line 231 thru line 254 to cylinder I29 to shift piston I 28 and locating feeler I into operative position relative to a portion of work piece I5. Solenoid 26I may be energized also by manually operated two-pole switch 255 in parallel with switch I03. The poles of said switch are opened and closed alternately. In response to movement of piston I28, arm I26 shown as a cam in Fig. 10, actuates normally open switch I which completes a circuit from line I thru the normally closed pole of switch I32 to energize solenoid 2T0. Said solenoid shifts a reversing valve 21! to the left against spring 212 to direct fluid from line 23'Ic thru line 273 to the left end of cylinder 20 to shift piston 2I and carriage II to the right. Another solenoid 216 when energized shifts said valve to the right against spring 211 to direct "fluid under pressure thru line 218 to the right end of cylinder 23. The operation of said solenoid 2'15 will be described later. After the actuation of solenoid 2T0, carriage II moves to the right until a portion of work piece I5 engages locating feeler I20 and shifts it far enough to actuate switch I32. Said switch thus actuated opens the circuit from line I thru normally open contact of switch I30 to deenergize solenoid 210, releasing valve 21! which is shifted to central position by spring 2112 to stop carriage I I with work piece I5 in proper location relative to grinding wheels 3|. Actuation of switch I32 also closes a circuit thru the normally open contacts thereof. This circuit connects line I thru switch I32 and switch 255, thru normally closed timer relay contact 200 to start timer motor 202. The time cycle however does not begin until later when the clutch solenoid is energized. Said circuit also energizes relay 280. One of the three normally open contacts 28I completes part of a circuit thru rapid feed solenoid I52. The rest of the circuit is completed upon withdrawal of gauge I20 when cam I 26 releases switch I30 to close the normally closed contact thereof. Another contact 2S2 completes a circuit to energize relay 256. The circuit to locator solenoid 25I thru the normally closed contact 255 of relay 255 is opened and the relay is held thru the normally open contact 25!. Deenergizing solenoid 26I permits spring 203 to shift valve 262 to direct fluid thru line 265 to shift piston I28 and locating feeler I20 to inoperative position. The third normally open contact 283 of relay 280 provides a holding circuit thru timer contact 205 and footstock switch I03 after the locating feeler has been returned to inoperative position.

Rapid feed solenoid I62, when energized, shifts valve IEO to the left directing fluid under pressure from line 231 thru line 290 to the rod end of cylinder I-II to shift piston I and wheel base 30 rapidly toward grinding position. Exhaust fluid from the other end of said cylinder may be directed thru a normally open bypass valve I42 from which it is directed thru line 29I to valve I 50 .and then thru passage 292 and exhaust manifold 293 to exhaust line 260. Fluid under pressure in line 290 enters cylinder 300 in which a piston 30! is slidably mounted and shifts said piston against spring 302 to close switch I47. Closing switch I41 has the same effect as closing the normally open contacts of switch 230 as described above. However, in addition to starting the headstock motor I8, relay 2-35 thru normally open contact 305 energizes relay 3I0. Said relay is held thru its normally open contact 3| I. In the line between line II and said contact is a plugging or brake switch 3I2. Energizing relay 3I0 closes the normally open contact 3 I 3 thereof which completes a circuit thru relay 243. Said circuit is held thru normally open contact 242 of aid relay, line 240, loader switch 50 and line 24I. A normally closed contact 3l4 of relay 3I0 is opened at this time. Said contact 3l4 is in a circuit parallel to that which includes the normally closed contact of loader switch 50.

As piston I40 and wheel base 30 move rapidly toward the work, switch I45 is released to energize solenoid I44 which shifts valve I42 to prevent the exhaust of fluid therethru from cylinder I4I. Said exhaust fluid must then escape thru throttle valve I43 which is set fora feed rate suitable for grinding crank checks or shoulders. As the wheel approaches the peripheral surface to be ground, switch I58 is released, deenergizing solenoid I55 and permitting spring I51 to shift valve I55 to the right. In this position, said valve directs fluid under pressure from line 2311) thru line I52, and throttle valve I53 to the head end of slow feed cylinder I5I to start the grinding feed. A relief valve I54 in line I52 is set for a pressure low-er than the pressure in the system but sufiicient for operating the slow feed mech anism. This prevents undue strain on the parts of said mechanism. Switch I58 also completes a circuit to energize clutch solenoid 204 to start the operation of the timing mechanism, the timing motor 202 having been started at the same time as the rapid feed.

The operator waits until he think that the portions being ground have been sufliciently rounded out and then shifts valve 90 to the left. This operation could be included in the automatic cycle but it is preferable to leave the time for initiating same to the judgment of the operator. Fluid under pressure from line 231a enters chamber I89, radial passage 95 and axial passage 9'! from which it is discharged thru radial passage 98 and chamber I23 to passage I80. Fluid under pressure in passage I is directed by valve I'Il thru either of the passages I or I86 to opposite ends of valve In to reciprocate same. Fluid in passage I80 is directed by valve II2 thru passages IS? and I88 to opposite ends of valve III to effect reciprocation thereof. Valve I'I2 receives fluid from branch passages I8I and I82 of passage I80. Fluid in said branches must pass thru pressure reducing valves I83 and I84 each of which may be adjusted for different pressures depending upon the requirements of the corresponding work engaging mechanism. Fluid from said branch passages is directed alternately by valv I12 thru passages I and I9! to back rest adjusting motors H53 and I74 respectively. Said motors are thus given a pulsating movement as described in the above mentioned application Serial No. 274,439. The frequency of said pulsations may be controlled by throttle valve I89 in passage I88 which alternately controls the supply of fluid to and the exhaust from one end of valve Ill thus controlling the rate of movement of said valve and the frequency of reciprocation of valve I12.

, At the end of the grinding period the timing contacts are opened, timer motor 262 is stopped and rapid feed relay 28B is deenergized due to opening of tim-er contact 285 in the holding circuit of said relay. If it is desired to stop the grinding operation before the end of the grinding cycle, relay 280 may be deenergized by opening the cycle return switch 268 in the circuit with the timer contact 205.

Deenergizing relay 28% opens the circuit thru contacts 282 to relay 256. However, relay 256 is kept energized by the holding circuit thru normally open contact 25?.

The circuit thru contact 28f of relay 2% upon opening deenergizes rapid feed solenoid :52. Spring It! then shifts valve Hi6 to the right to the position shown in Figure 10. Fluid under pressure is directed from line 237 thru line 29! and check valve 295 to cylinder i4! causing piston if! to move wheel support 38 to separate work piece 15 and wheels 3!. Fluid under pressure in line 29i passes thru line 294 and enters the rod end of cylinder i5| to reset piston I58 and the slow feed mechanism. At the same time switch IE8 is actuated to deenergize solenoid I58 and open the circuit to timer motor 282. Valve E55 is then shifted to the right by spring I51 to prevent further passage of fluid under pressure from line 231?) to line I52. Exhaust fluid from the other end of cylinder 55! passes thru passage I59 to valve ifiii from which it is discharged thru exhaust passage 2%, and manifold 293 to exhaust line 25a. The exhaust passage might be dispensed with and the exhaust fluid pass out thru relief valve 154 which is set for a much lower pressure than the rest of the system.

As the rearward movement of wheel base 33 continues, switch I45 is actuated to deenergize solenoid 144. spring 148 may then reset valve I42 to its normal position, i. e. open to bypass exhaust fluid around throttle valve I43.

Pressure switch I41 remains closed under the exhaust pressure in line 298. When the rearward movement of the wheel base is completed, spring 392 will shift piston SUI to open the circuit thru said switch. Relay 235 will be held thru contact 343 thereof until tappet switch 394 is opened by rotation of the headstock spindle whereupon said relay will be deenergized. Contact 305 in the circuit to relay 310 will be opened but said relay will be held by a circuit thru its own contact 3. Normally closed contact 30'! of relay 235 will complete a circuit thru said contact 3 to reverse relay 234. Said reverse relay, upon being energized, will cause motor I8 to start rotation in the opposite direction. However, such reverse rotation immediately opens plugging switch 312 in the holding circuit of relay 3i0 and also deenergizes reverse relay 234 thru the normally closed contact 30'! of relay 235 to stop motor 18.

Deenergizing relay Sill opens the circuit thru contact 313 to relay 243 but said relay is held by the circuit thru loader switch 68 and lines 249 and 24l Line 241 is connected to line 5 thru the normally open contact 242 of relay 243. Deenergizing said relay 3N also closes the normally closed contact 3M which completes a circuit from line I through contact 242 to energize footstock solenoid 88. Said solenoid shifts valve 86 against spring 81 to direct fluid under pressure from line 231a thru line 259 to withdraw rootstock center l1. Bracket 15 on'said center is effective thru rod 10 and disk H to shift work piece [5 off of headstock center IS. The work being thus freed of the centers, the springs 46 and 47 and 52 and 53 of the loading device will lift it out of grinding position and. carry it back to a point where the operator may remove it and replace it with an unground piece.

At the time when footstock solenoid 88 is energized, carriage control solenoid 218 is also energized. Said carriage solenoid shifts valve 2|! to the right and directs fluid under pressure thru passage 218 to shift piston 2| and carriage II to the left to loading position.

Movement of the loading device to inoperative position permits switch 68 to return to normal position as shown in Figure 11. Thus the circuit thru lines 246 and 24! is opened and relay 243 is deenergized. With switch 68 in normal position, footstock solenoid 88 and. carriage control solenoid 276 are both energized and the valves actuated thereby are so positioned as to direct fluid under pressure to hold footstock center I! and carriage II in inoperative positions.

Fluid under pressure in said line 250 also passes thru line to shift valve 96 to the right. This movement opens passage [15 to the fluid which shifted said valve and said fluid is thus directed to back rest motors I13 and I74 to rotate same in a counter-clockwise direction and thus reset the work engaging members of said rest.

We claim:

1. In a metal working machine, a work support having a headstock and footstock mounted thereon, work supporting centers in said headstock and footstock, a loading mechanism for placing a work piece in operative position including a pivoted work receiving member having resilient means for lifting said work away from said centers, said resilient means being just strong enough to overcome the weight of the work piece and having sufficient movement to return said work to inoperative position.

2. In a metal working machine, a support having a cutting tool mounted thereon, a work support having a headstock and a footstock mounted thereon, work supporting centers in said headstock and said footstock, mechanism for shifting one of said centers axially whereby to engage a work piece and move same into operative relation with the other center, a gauge member movable toward and from operative position for determining the relative axial positions of the work piece and the cutting tool, and means responsive to the shifting of said center for moving said gauge member into operative position.

3. In a metal working machine, a tool support movable toward and. from a work piece and having a cutting tool mounted thereon, a work support, means for rotatably supporting a work piece thereon, means for moving said work support and said tool support relatively longitudinally, means for relatively locating the work and tool axially including a gauge movable toward and from work position and having means for co-acting with a locating surface on said work piece, and means responsive to movement of said gauge into working position for causing a relative longitudinal movement between said tool and said work whereby to position said tool and work for machining.

4. In a metal working machine, a tool support movable toward and from a work piece and having a cutting tool mounted thereon, a work support, means for rotatably supporting a work piece thereon, means for relatively locating the work and tool axially including a gauge movable toward and from working position and having means for co-acting with a locating surface on said work piece, means for causing a relative longitudinal movement between said tool and said work, and mechanism actuated by said gauge when said tool and said work reach a predetermined position for stopping said longitudinal movement.

5. In a metal working machine, a tool support movable toward and from a work piece and having a cutting tool mounted thereon, a work support, means for rotatably supporting a work piece thereon, mechanisms for effecting relative transverse and longitudinal movements of said supports, means for relatively locating the work and tool axially including a gauge movable toward and from working position and having means for co-acting with a locating surface on said work piece, means for causing operation of said mechanism for effecting relative longitudinal movement between said tool and said work, and mechanisms actuated by said gauge when said tool and said work reach a predetermined position for stopping said longitudinal movement and for returning said gauge to inoperative position.

6. In a machine of the kind set forth in claim 5, means responsive to the return of said locating gauge for actuating said transverse moving mechanism for causing a feeding movement between said tool and said work piece.

In a machine of the kind set forth in claim 5, means responsive to the return of said locating gauge for actuating said transverse moving mechanism for causing a feeding movement between said tool and said workpiece and a size control mechanism for actuating said transverse moving mechanism to separate said work and tool at a predetermined point in the machining operation.

8. In a metal working machine, a tool support, a cutting tool mounted thereon, means for efiecting a transverse movement of said support toward and from a work piece, a work support, means, for rotatably supporting a work piece thereon, including a headstock and a footstock having centers for engaging a work piece, a loading mechanism for placing a work piece in and removing same from operative position, means for relatively locating the work and tool axially including a gauge movable toward and from working position and having means for acting with a locating surface on said work piece, means responsive to movement of said gauge into working position for causing a relative longitudinal movement between said tool and said work, mechanisms actuated by said gauge when said tool and said work reach a predetermined longitudinal position relative to one another for stopping said longitudinal movement, withdrawing said gauge to inoperative position and initiating movement of said tool toward a work piece, a size control mechanism, and means actuated thereby when a work piece has reached a pred e-. termined size for releasing said loading mechanism to remove said work piece from operative position.

9. In a metal working machine, a tool support, a cutting tool mounted thereon, means for effecting a transverse movement of said support toward and from a work piece, a work support, means for rotatably supporting a work piece thereon, including a headstock and a footstock having centers for engaging the work piece, a

loading mechanism for placing a work piece in and removing same from operative position, means for relatively locating the work and tool axially including a gauge movable toward and from working position and having means for coacting with a locating surface on said work piece, means responsive to movement of said gauge into working position for causing a relative longitudinal movement between said tool and said work, mechanisms actuated by said gauge when said tool and said work reach a predetermined longitudinal position relative to one another for stopping said longitudinal movement, withdrawing said gauge to inoperative position and initiating movement of said tool toward a work piece, a size control mechanism, and means actuated thereby when a work piece has reached a predetermined size for withdrawing said footstock center thereby releasing said loading mechanism to remove said work piece from operative position.

10. In a metal working machine, a tool support, a cutting tool mounted thereon, means for effecting a transverse movement of said support toward and from a work piece, a work support, means for rotatably supporting a work piece thereon, including a headstock and a footstock having centers for engaging the work piece, a loading mechanism for placing a work piece in and removing same from operative position, means for relatively locating the work and tool axially including a gauge movable toward and from working position and having means for co-acting with a locating surface on said work piece, means responsive to movement of said gauge into working position for causing a relative longitudinal movement between said tool and said work, mechanisms actuated by said gauge when said tool and said work reacha predetermined longitudinal position relative to one another for stopping said longitudinal movement, withdrawing said gauge to inoperative position and initiating movement of said tool toward a work piece, a size control mechanism, and means actuated thereby when a work piece has reached a predetermined size for releasing said loading mechanism to remove said work piece from operative position and for returning said work support to inoperative position,

11. In a metal working machine, a tool support, a cutting tool mounted thereon, means for effecting a transverse movement of said support toward and from a work piece, a work support, means for rotatably. supporting, a work piece thereon, means for relatively locating, the work and tool axially including a gauge movable toward, and from working position and having means for co-acting witha. locating surface on said" work piece, means for causing a relative longitudinal movement between saidtool and said work to locate said parts for a cutting oper ation, and means responsive to withdrawal ofsaid gauge for initiating movement of said tool toward said work piece.

12. In, a metal working machine, a tool support,,a cutting tool; mounted thereon, means for effecting a transverse movement ofsaidsupport toward and from a work piece, a work support, means for rotatably supporting a; work piecethereon, means for relatively locating; the-work and tool axially including, a gauge movable toward and" from working position and having means for co-acting with; a locating surface-onsaid work piece, means for-causi'ngarelative-longitudinalmovement-between said tool-and said work to locate said parts for a cutting operation, and interlocking means for effecting withdrawal of said gauge and for initiating movement of said tool toward said work piece.

13. In a metal working machine, a support having a cutting tool mounted thereon, a work support, means for rotating a work piece thereon including a headstock and footstock, an axially movable center in said footstock, mechanism for efiecting relative feeding and longitudinal movements of said supports, a motor for moving said footstock center toward and from operative position, a loading device for placing a work piece in alignment with said footstock center, means operable when said loading device has moved a work .piece into position for effecting operation of said footstock center to engage said work piece and to shift same into operative relation with said headstock, means for locating the work laterally relative to the cutting tool including a gauge member, a motor operable in response to movement of said loading mechanism for moving said gauge member into and out of operative position relative to a selected surface of the work piece, means operable after said gauge has moved into position for initiating movement of said work support to cause the locating surface on a work piece to move toward said gauge, means operable when said surface reaches a predetermined position for withdrawing said gauge and for initiating said relative feeding movement to bring the cutting tool into operative relation with a work piece and for actuating said work rotating means, a size control mechanism, means actuated thereby when the work has been ground to a pre determined size for separating said cutting tool and work, means actuated by said separating movement for stopping rotation of the work, withdrawing said footstock center, and returning said work support to starting position, and means operable in response to withdrawal of said center for causing said loading device to remove said work piece from operative position.

14. In a metal working machine, a work carriage, a tool support, a cutting tool mounted thereon, mechanisms for effecting relative transverse and longitudinal movements of said support and said carriage, mechanism for rotatably supporting a work piece on said carriage, means for actuating said work supporting mechanism to engage and support a work piece, a device for locating said work piece and said cutting tool axially of one another, means whereby operation of said transverse and longitudinal moving mechanisms, said work supporting mechanism, and said locating mechanism are actuated in a predetermined sequence, and means for initiating said sequence by placing a work piece in the machine.

15. In a metal working machine, a work carriage, a tool support, a cutting tool mounted thereon, mechanisms for effecting relative transverse and longitudinal movements of said support and said carriage, mechanism for rotatably supporting a work piece on said carriage, means for actuating said work supporting mechanism to engage and support a work piece, a device for locating said work piece and said cutting tool axially of one another and in operative relation, means whereby operation of said transverse and longitudinal moving mechanisms, said work supporting mechanism, and said locating mechanism are actuated in a predetermined sequence, means for initiating said sequence by placing awork piece in the machine, a size control mechanism and means actuated thereby for separating said work and tool, and mechanism responsive to said separating movement for removing said Work from the machine and for initiating said longitudinal movement whereby to return said carriage and said tool to inoperative relation.

16. In a metal working machine, a tool support, a cutting tool mounted thereon, a work support, means for rotatably supporting a work piece thereon, mechanism for effecting a, relative transverse movement between said supports at a rapid rate to position said tool and work in operative relation, mechanism for thereafter effecting said transverse movement at a slower rate for cutting, a size control mechanism including a timing device, and means responsive to said transverse movement for starting said timing device and said slow transverse movement at substantially the same time whereby to determine the duration of a machining operation.

17. In a metal working machine, a support having a cutting tool mounted thereon, a work support having a headstock and a footstock mounted thereon, mechanism for effecting a relative transverse positioning movement between said supports, work supporting centers in said headstock and said footstock, mechanism for shifting one of said centers axially whereby to engage a work piece and move same into operative relation with the other center, a gauge member movable toward and from operative position for determining the relative axial positions of the work piece and the cutting tool, and means for efiecting withdrawal of said gauge and for initiating operation of said transverse positioning movement. 7

18. In a metal working machine, a work support, a loading mechanism for placing work in and removing same from operative position, resilient means for holding said loading mechanism in inoperative position, means for holding the work in operative position against the action of said resilient means including a headstock and a footstock each having a center for engaging and supporting the work piece, means for retracting one of said centers, said resilient means being operable upon withdrawal of said center for returning said work and loading mechanism to inoperative position.

19. In a metal working machine, a tool support movable toward and from a work piece and having a cutting tool mounted thereon, a work support, means for rotatably supporting a work piece thereon, mechanisms for effecting relative transverse and longitudinal movements of said supports, means for relatively locating the work and tool axially including a gauge movable toward and from working position and having means for co-acting with a locating surface on said work piece, means for causing operation of said mechanism for elfecting relative longitudinal movement between said tool and said work, mechanisms actuated by said gauge when said tool and said work reach a predetermined position for stopping said longitudinal movement and for returning said gauge to inoperative position, and mechanisms operable in timed relation with said gauge return movement for actuating said transverse moving mechanism.

20. In a metal working machine, a tool support movable toward and from a work piece and having a cutting tool mounted thereon, a work support, means for rotatably supporting a work piece thereon, mechanisms for effecting relative transverse and longitudinal movements of said supports, means for relatively locating the work and tool axially including a gauge movable toward and from working position and having means for co-acting with a locating surface on said work piece, means for causing operation of said mechanism for effecting relative longitudinal movement between said tool and said Work, mechanisms actuated by said gauge when said tool and said work reach a predetermined position for stopping said longitudinal movement, for returning said gauge to inoperative position, and for actuating said transverse moving mechanism to cause the tool to be moved to operative position.

21. In a metal working machine, a Work support having means thereon for rotatably supporting a work piece, a loading mechanism including a member movable from a remote inoperative position to a position adjacent said rotatable work supporting means, means for normally holding said member in said inoperative position, a work carrier mounted on said member, means for holding said work carrier in position with the work piece out of alignment with said rotatable supporting means when said member is in operative position, said carrier being movable therefrom to place said work piece in alignment with said rotatable supporting means.

22. In a metal working machine, a work support having means thereon for rotatably supporting a work piece, a loading mechanism including a pivoted member movable from a remote inoperative position to a position adjacent said rotatable work supporting means, resilient means for normally holding said member in said inoperative position, a work carrier pivotally mounted on said pivoted member, means for yieldingly holding said Work carrier in position with the work piece out of alignment with said rotatable supporting means when said pivoted member is in operative position, said carrier being movable against said yielding means to place said work piece in alignment with said rotatable supporting means.

23. In a metal Working machine, a work support having a headstock and footstock mounted thereon, work supporting centers in said head stock and footstock, a loading mechanism for placing a work piece in operative position including a movable Work receiving member having means capable of exerting just enough force to overcome the weight of the work piece, said Work receiving member being movable from a position for receiving a work piece to a position for engagement of said work piece by said centers.

24. In a metal working machine, a tool support, a cutting tool mounted thereon, a work support, means for rotatably supporting a work piece thereon, mechanism for eiTecting a relative transverse movement between said supports at a rapid rate to position said tool and work in operative relation, mechanism for thereafter effecting said transverse movement at a slower rate for cutting, a size control mechanism including a timing device, and means operable substantially at the end of said transverse positioning movement for starting said timing mechanism.

HUGH N. ROCKS. MILBURN A. HOLLENGREEN. HAROLD E. BALSIGER.

Images