US2333304A - Surface finishing machinery - Google Patents

Description

Nov. 2, 1943. H. ERNST ET AL 2,333,304

SURFACE FINISHING MACHINER Y Filed Jan. 25, 1940 9 Sheets-Sheet 1 Nov. 2, 1943. H. ERNST ET AL 2,333,304

SURFACE FINISHING MACHINERY Filed Jan. 25, 1940 9 Sheets-Sheet 2 ATTORNEY.

Nov. 2, 1943. I H. ERNST ET AL 2,333,304

SURFACE FINISHING MACHINERY Filed Jan. 25, 1940 9 Sheets-Sheet 3 WWW ATTORNEY Nov. 2,1943. H. ERNST ET AL 2,333,304

SURFACE FINISHING MACHINERY Filed Jan. 25, 1940 9 Sheets-Sheet 4 Nov. 2, 1943. H. ERNST ETAL 2,333,304

SURFACE FINISHING MACHINERY Filed Jan. 1940 9 Sheets-Sheet 5 17a 7 7/ .44 x

V s Q a Nov. 2, v1943. H. ERNST ETAL 2,333,304

SURFACE FINISHING MACHINERY Filed Jan. 25, 1940 9 Sheets-Sheet 6 fix INVENTOR. /7/4/x; 597.57 BY (425520752411 Nov. 2, 1943. H. ERNST ET AL 2,333,304

SURFACE FINISHING MACHINERY Filed Jan. 25, 1940 9 Sheets-Sheet 7 Wm ATTORNEY,

Nov. 2, 1943. H. ERNST ETAL 2,333,304

SURFACE FINISHING MACHINERY Filed Jan. 25, 1940 9 Sheets-Sheet 8 O O Y N H. ERNsT ETAL. 2,333,304

SURFACE FINISHING MACHINERY Filed Jan. 25, 1940 9 Sheets-Sheet 9 Zia? Patented Nov. 2, 1943 UNITED STATES PATENT OFF ICE SURFACE FINISHHIG MACHINERY Application January 25, 1940, Serial No. 315,510

36 Claims.

This invention relates to improvements in surface finishing machinery and has particular reference to improvements in machines intended for producing a final surface finish of high-degree of accuracy, particularly on metal articles of substantially circular form in cross section.

The initial machining of such articles or work pieces in its final stages is normally effected as a grinding operation, although in some instances the present invention is utilizable directly to produce a finished surface on an article previously shaped as by turning, broaching or the piece.

It is, therefore, one of'the principal objects of the present invention to provide a machine which will effect through cold cutting a maximum abrading action of a character to remove this nap or other irregularities resulting from the previous machining operation.

A further object pf the present invention is the provision of a machine capable of effecting multiple relative movements of an abrading member or members and the surface of the work to prevent repetitious engagement between corresponding portions of the abrading member and work which might otherwise result in reproduction or perpetuation of certain of the surface scratches or irregularities.

A further object of the present invention is the provision of an improved machine, particu larly adapted for operation upon .cylindricalor other work pieces of circular or substantially circular form in cross section which will effect a relative multi-directional scrubbing motion in constantly changing direction between the tool and work piece whereby to eliminate visible scratches and hill and valley effects on the surface of the work piece.

An additional object of the presentinvention is the provision of a machine having the capacity for effecting relative rotary and oscillatory movements of the interengaged tool and work piece elements in a smooth manner, while effecting an appreciable rate of cut speed resultant from said movements,

Additionally, the present invention contemplates the provision of an improved machine capable of alternative employment for either ultimate finishing or combined roughing and finishing operations in which the several parts shall be r capable of ready relative adjustment to accom-- modate varying lengths and diameters of work pieces or portions of work pieces to be individually or simultaneously operated upon and in which the series of tool holding elements may be satisfactorily controlled individually and selectively or in unitary groups.

Other objects and advantages of the present invention should be readily apparent by reference to the following specification, considered in conjunction with the appended drawings illustrating one embodiment of the principles thereof, and it will be understood that any modifications or variations may be made in the specific structural details and combination of elements hereinafter described within the scope of the appended claims without departing from or exceeding the spirit of the invention.

Figure 1 represents a front elevation of a machine constructed in accordance with and embodying the principles of the present invention.

Figure 2 is a top plan view thereof.

Figure 3 is a vertical sectional view taken as on the line 33 of- Figure 1.

Figure 4 is an enlarged vertical section on the line 4-4 of Figure 3.

Figure 5 is a vertical section as on line 55 of Figure 4.

Figure '6 is a fragmentary transverse sectio as on line 6-6 of Figure 4.

Figure 7 is a vertical section through one of the tool holding elements and related parts of the machine as on the line 'l-l of Figure 1.

Figure 8 is a sectional view through the tool mechanism at right angles to Figure 7 as on the line 8-8 thereof.

Figure 9 is a section with parts broken away as on the line 9-9 of Figure 7.

Figure 10 is a vertical sectional view as on the line l0|0 of Figure 2.

Figure 11 is a vertical section through the head stock driving motor as on the line H--I| of Figure 10.

Figure 12 is a similar view largely in section, illustrating the interporting connections for sup ply and exhaust of actuating medium as respects the chambers and rotary valves of the motor.

Figure 13 is a similar view illustrating the interporting of a diiferent series of conduits of,

Figure 17 is a vertical sectional viewthrough the oscillation pumps as on the line l|-l'l of Figure 3.

The machine chosen for purposes of illustration comprises a bed or support 28 having mounted thereon a longitudinally traversable table 26 on which is suitably adjustably mounted.

the headstock unit 21 having a driving spindle 28 for engagement with the work piece 28, whose other end is supported by the center 88 of the adjustable tailsiock mechanism 3|.

Depending from the table 26 is a bracket 32 connected to piston rod 83 (Figure 17) of the reciprocating hydraulic motor 84 controllable as hereinafter described for eflecting longitudinal reciprocations of the table and work piece supported thereon. Mounted on the bed at each side of the work piece are the platens 85 and 86 of similar oppo- 'sitely arranged form, having the depending dovetail lugs 31 interengageable with the dovetail ways 38 oi brackets 88 on the bed. A central guide pin 48, particularly illustrated in Figures 4 and 7 of the drawings, has a head portion slidably engaged in groove 4! of the platen, permitting of in and out movement of the latter but restraining same against shifting longitudinally with respect to the supporting bracket 38. The platens 85 and. 36 are each formed with recesses 43 receiving slide blocks 44 actuable by eccentric pins 46 on the stub shafts 46 which are disposed in pairs-one near each end of the platen.

Guide brackets 4'! guide the platen for in and out movement, while preventing tilting or twisting thereof. Members 46 extend downwardly i'rom the bracket support and have secured or formed thereon pinions 48 (Figure 5) engaged by-rack portions 48 of the double end piston rod 58 having a piston portion 5| reciprocable in cylinder 52.

By reference particularly to Figures 4 to .6 inclusive it will be readily understood that reciprocation of the piston will move the racks 48 in one direction or the other, correspondingly oscillating members 46 to displace blocks 44 either inwardly or outwardly, and thus efl'ect corresponding shifting of the associated platen 36.

These platens have adiustably supported thereon as by. clamp bolts 58 selectivelyengageable longitudinally and transversely in the T-slots 64, the tool holders 68 particularly illustrated in v Figures 7 and 8. These, it will be noted, are

operation on a selected portion of the work piece while the series of units are Jointly actuated of slot in the sliding member 60. The inner portion of the tool holder sleeve is provided with a head 64 having ways 65v for the anti-friction bearings 66 mounting block 61 for transverse reciprocation. Block 61 has a seat or socket 68v to receive the abrasive tool 69 in the form of an extremely fine abrasive block or stick. An adjustable gib 18 clamped asby screw '|lserves rigidly to secure the abrading member within the seat.

Formed in the head 64, extending parallel with the ways 65, is a cylindrical bore or motor chamber 12 in which is slida'ble the piston 13 inter-' engaged by stud 14 with the abrasive holder 61. The piston has a recess 15 at one end to receive the elongated actuating spring 16 and at. th other end has a second recess 11 containing a bufler spring 18. A passage 18 communicating with the chamber 11 serves to transmit actuating fluid pulsations from one of the pistons 88 shown in Figure 16 to react on the piston 13. As a pulsation of the hydraulic actuating medium is forced into this end of cylinder I2. the piston 13 will be forced downwardly as viewed in Figure 8 against the resistance of spring 16, while as the pressure pulsation is released the spring will expand; moving the piston in the opposite direction, its reverse movement being yieldingly restrained by the bufler spring 18.

It will thus be'noted that in addition to their individual positional adjustments" the series of tools and holders therefor respectively at the front and the rear of the machine are each 'adjustabie as a group in a direction toward and away from the interposed work piece 29, and are also individually, yieldingly urged into operative engagement with the work piece as well as sup ported for individual reciprocating movements in a direction parallel with the axis of the work piece.

v For most satisfactory finishing it is ordinarily desirable that a cutting medium or 011 be constantly supplied in a manner tending to produce an interposed fllm between the work and operative surface of the tool. This is eflectable, for example, by coupling to'each of the heads 64 a flexible conduit 8| connected tosupply' line 82 of the cutting fluid and lubrication circulating system, Figure 15, which includes reservoir 83 and pressure pump 84 for eflecting circulation of the medium. This conduit is connected by the interdrilled passage 85 to port 86 of the cutting fluid transmitting passage 81 formed in stud l4 and thence distributed through passage 08 and aperture 88 in the face of the abrading member to the surface of the work at a point centrally oihilge engagement of the abrading member therew v The pressure exerted by spring 6| for forcing the abrading member into, engagement with the work is adjustable as by screw 98. As the abrading member wears down the high spots on the work surface and the surface approaches smoothness, dynamic conditions created by the relative movement of the abrading member with respect to the work piece generate fluid film pressures which tend to separate the two in a manner similar to a lubricated bearing, thu's causing decreased abrading action. Additionally, static fluid pressures can be imposed through aperture 89 to the abrading surface, thus supplementing the generated dynamic pressures and permitting the control of the separation of the abrading member and the work by the operator to suit the conditions of work material and stone action. The application of cutting fluid through the stone has the two-fold purpose of first application of fluid directly at the points of abrasion,

and secondly, the application of static fluid pres-- sures at the will of operator to supplement the dynamically generated pressures.

Mention has been made of the fact that the work piece 21 is illustrated as supported for longitudinal shifting movement by table 26 and has coupled therewith a driving spindle 28. To attain most effective results in performance of the finishing operation it has been found desirable to impart to the work, in addition to it longitudinal or axially traversing movement, a compound movement about its axis which can best be defined as a motion .of rotation having superimposed thereon a' motion of rotary oscillation. This is accomplished by ffecting'a potential actuation of the headstock motor 9I in a constant direction at a uniform rate of rotation and then providing additional mechanism alternately reacting positively and negatively on this headstock motor to effect successive pulsations of acceleration and deceleration. In this manner a uniform number of revolutions per minute of the work piece is efiected but by a back and forth progressively advancing oscillation of the work instead of a constant and uniform rotation thereof, whereby the relative scrubbing action or effective relative movements of the work surface and abrading member is greatly improved and maximum variance in relative directional movements of work surface and individual abrasive particle is attained.

In, a preferred form, the frequency ratio between rotary oscillations of the work and longitudinal reciprocations of the abrading member may be two to one and in such a phase relation that a figure eight type of progressively advancing spiral path is, traversed by an individual abrasive particle on the urface of the work with constant reversal of effect between thewprk surface and any of the multiplicity of cutting facets of the. abrasive particle. This particular path, eifectable by the several potential movements of the parts of the machine at the relativ two to one ratio of reciprocations and oscillations above referred to, has been indicated in Figure 14. In an alternative form the frequency ratio may be one to one and the phase difference 90, thus providing a relative path for the abrasive grain which is generally circular, where the amplitudes are equal, and elliptical where the amplitudes are unequaL. In another alternative form the frequency ratio may be slightly less than one to one,thus giving a constantly changing path.

Certain structural details of the headstock motor suitable for effecting the composite move ment of the work piece just referred to have been illustrated in Figures 10 to 13 inclusive. From this it will be noted that the. driving spindle 28 of the headstock is carried in a main spindle or shaft 92 suitably supported in anti-friction bearings 93.

Keyed on member 92 is the bushing 94 having suitable splines in interengaged driving relation with the motor body 95. This body has a multiplicity of radial grooves or slots 96 formed therein which, in the present instance, are shown as I4 in number. slidably engaged in each of these slots is the blade 91 outwardly urged as by springs 98 and having rollers "99 riding on the lobed inner surface of the ring I00. This ring is retained between the end plates IOI and I02 andis preferably symmetrically hollowed to provide the crescent-shaped chambers I03, I04, I05 and I08 into which upon relative rotation of the rotor the several blades 91 are successively forced by their actuating springs 98.

For effecting actuation of the motor body in either direction, there have been provided a first series of circumferentially elongated ports I01, shown as four in number, respectively disposed each at one end of the arcuate chambers I03 while at the opposite end of the chambers are similarly shaped ports I08. The ports I0'I-as indicated in Figure 10--are coupled by grooves I09 with inner circular ports IIO while the ports I08 are connected by grooves III with the inner circular ports IIZ.

The function of the ports Ill) and I I2 and the slots I09 and Ill connecting them to the circumferentially elongated slots I01 and I08 is to keep the same pressure on the end of blade 91 which is toward the center and also the roller 99 which bears against the outer end of blade 91.

It is necessary to keep these pressures equal in order not to build up a force at blade 91 against slot 96 which would produce a friction force that would prevent the blade 91 and roller 99 from moving radially when they are passing an exhaust or a pressure port I01 and I08.

Ports H0 and H2 and the connecting slots I09 and III also serve as a passageway to permit inlet or outlet of oil under the blades 91 during the time that they are moving radially while the blade and roller are rotating past an exhaust or a pressure port I 01 or I08. When the blade 91 and roller 99 rotate to such a position that the end of the pressure or exhaust port I01 and I 08 is reached, the ports H0 and H2 are also cut oif and the bottoms of the blades 91 are then connected to a new set of ports 2' which are connected to an annular groove 3' which is connected to pump pressure through line H4, Figure 16. Therefore, the blade 91 is maintained in contact with roller 99 and the latter with ring I 00 while rotating between the ports I01 and I08 in chambers I03, I04, I05 and I06.

For suitably coupling the conduits for pressure actuating medium with the porting groups I01 and I08, the motor head MI is provided with multiple interdrilled passages as will be best understood by reference to the sectional views, Figure 12 and Figure 13. Figure 12 has been taken as on the section line I2--I2 of Figure 10 and indicates the interconnected passages H3, H4 and H5 communicating as by the passages or drillings indicated at I I6 with the series of portings I08. These passages are in turn suitably connected with the supply conduit II1 through passage II8.

A second series of interdrilled passages II8', II9 and I20 formed in the head IOI, as shown in Figure 13, connects with the several portings I01 to convey the exhaust actuating fluid from the supply line.

motor to discharge conduit I2 I. It is to be particularly noted that the arrangement of sliding vanes and multiple pressure ports is such that at all times there are one-or more vanes in intermediate position within each of the pressure chambers such as I03, I04 in position for reaction thereagainst of the pressure conditions existing in both the portings I01 and I08. It will further be noted that by the combination and arrangement of vanes and pressure chambers shown there will be maximum effective torque reaction of a sensitive character on the shaft 92 for effecting its combined rotary and imposed rotary oscillatory movements and transmitting same to the work in a smooth manner.

For specific understanding of the manner in which these movements are imparted to the work driving motor, attention is invited to the hydraulic circuit diagram as particularly illustrated in Figure 16 of the drawings. There is there shown as coupleable with the hydraulic fluid input line II1, previously referred to, a uniflow pressure line I22 coupled and controlled by valving hereinafter described in detail with the pressure creating pump, I23, a check valve I24 preventing .reverse flow of fluid from the pressure The opposite side of the motor is coupled by conduit I2I with the balancing valve I25 from which it passes through the adjustable throttle portion I26 of valve unit I21 into exhaust conduit I28 having the adjustable back pressure valve I29 for maintaining suitable pressure in the system as an entirety for purposes which will be hereinafter described. Extending from pressure conduit I22 is a conduit I30 leading to the headstock selector valve unit I3I, con taining a valve member having an actuating portion I32 and a spool I33 which, in the position shown in Figure 16, couples pressure conduit I22 with conduit I34 extending to one of the oscillation control cylinders I35.

It should be stated at this time that the plunger-pump that causes rotary oscillation of the headstock spindle 92, Figure 10, is shown merely diagrammatically on the hydraulic diagram Figure 16.

Instead of only one cylinder I35 and piston I36 and opposing this only one cylinder I and piston I H, there are really four cylinders I35 and pistons I 33 spaced 90 apart in the right hand plane shown on Figure 17 and four cylinders I40 and pistons I4I spaced 90 apart in the left hand plane shown on Figure 17. Since all four of the cylinders I35 are connected together through interdrilling in the pump body, and also since all four of the cylinders I40 are likewise connected they act hydraulically as one pair of opposed cylinders; that is, one cylinder discharges oil when the opposite one is on the suction stroke.

The exact construction of the headstock oscillator plunger pump as shown on Figure 17 will be explained later. The hydraulic function of this pump is explained as follows:

Mounted in this cylinder I35 is a piston I36 having a follower riding against cam I31 on shaft I38 which is driven by the hydraulic motor I39 which determines control of the variousoscillator mechanisms of the present machine. Diametrically opposed to cylinder I35 is a second cylinder I40 having a piston I4I also provided with a follower engaging the cam I31. Springs I42 maintain the pistons in engagement with this cam which is formed with diametrically opposite high and low points so that the pistons will be shifted alternately and in timed relation in suction and compression strokes. Leading from cylinder I40 is conduit I43 coupled through valve unit I3I with the exhaust conduit I2I. of the headstock motor.

The valve I3I serves as a selector to determine whether the headstock motor is driven directly and entirely controlled by the pressure input through H1 and exhaust through I2I, which is the condition existing when the valve is inits inwardly pressed position, or whether the headstock is subject to superimposed hydraulic pulsations produced by the oscillator control mechanism when the valve is in the position shown in Figure 16 and the oscillator is connected in parallel with the input and'output sides of the motor.

The oscillator motor I39 is itself of conventional type actuated by hydraulic medium supplied from pressure line I22a and exhausted through conduit I44 which is coupled with the opposite side of the balancing valve I25 and passes through the throttle control portion I46 of valve I21 to discharge conduit I20.

As shown, the parts are so related that onethird of the total flow passes through the head stock motor for effecting rotation thereof while two-thirds is directed to the oscillator mechanism for effecting its rotation whereby the oscillator motor will rotate at a much higher rate of speed effecting a multiple number of strokes of the pistons I35I4I for each rotation of the headstock motor. By adjustment 'of resistances in valve I21 as by rotation of the control knob I41 the relative rotation of the two motors may be suitably controlled and varied.

From the foregoing it will be readily apparent that the input flow through conduit I I1 of itself and when the oscillator is short circuited by suitable adjustment of valve I3I serves to impart a constant and uniform rate of rotation to the headstock motor and thus to the work piece. When, however, 'the oscillator mechanism is coupledin parallel with the drive to the headstock motors, the action of the piston I35 serves alternately to add and subtract to the quantity of liquid in the system on the input side of the hydraulic motor, while action of the piston I4I counteracts the quantitative displacement of fluid on the exhaust side of themotor. As a result, at any period of time the actual movement of thehydraulic motor will be the algebraic sum of the flow of input fluid from pump I23 and the liquid displaced positively or negatively in effect by piston I35. For effective operation the unit displacement of the piston must be greater than the potential flow during such unit of measurement through input line II1. When piston I35 is moving in an inward or suction stroke it will require more fluid than is being supplied to the headstock motor by the pump I23, with the result that the fluid in the system displaced by the outward or pressure stroke of piston I I" will act to rotate the headstock motor in a counterclockwise direction. Upon reversal of strokes of the pistons by rotation of the oscillator motor and cam, the amount displaced by piston I35 will be additive to the amount continuously being supplied through line I I1 with the result that the headstock motor will then be rotated at an accelerated speed in a clockwise direction.

It will thus be seen that there is imposed on the headstock motor a movement of simple rotation at a predetermined number of revolutions per minute, together with a movement of super- 2,sss,so4 5 imposed rotary oscillation in which a plurality of successive clockwise and counterclockwise movements are imparted to the headstock motor during each complete rotative movement thereof.

The foregoing embody the essential elements of the present invention for effecting, as described, a combined longitudinal or axial hydraulically effected oscillation of a. multiple number of tool or abrading members, together with a relative bodily axial traversing or reciprocating movement of work piece and abrading members during which movement there is additionally imparted to the work piece the hereinabove described combined rotational and superimposed rotary oscillatory movements. In this manner a most efflcient and effective relative scrubbing action or movement of abrading members and work piece surface is effected with a continuous change of relative direction of movement between an individual abrasive particle on the tool and the work such that there is no dragging or repetitious movement of the abrasive and its various cutting edges, each being momentarily operated and then shifted in a manner to clear same from any chips which might tend to cause a built-up edge, producing scratches or imperfections .on the surface of the work.

The general hydraulic operation and control of the machine for effecting the foregoing results is diagrammatically illustrated in'Figure 16 of the drawings. As there shown, there is provided a reservoir I52 from which hydraulic medium is supplied for actuation of the machine through pressure line I53. A suitable relief valve I54 maintains the pressure in the system at the desired value and permits of return of excess volume to reservoir through exhaust line I55. The conduit I53 is directly coupled to the grooved and ported bushing I56 containing the start and stop valve plunger I 51 manually actuable as by move ment of lever I58. With the parts in the stop position shown, the pressure is coupled by groove I59 with the return system I60 which i connected to one side of the left hand or rear platen control cylinder 52, shifting the rod 50 in a manner to cause retraction of the platen. It is further provided .with a branch I60a having a pilot portion I60b eifective to shift valve I6I in an upward position as shown, thereby coupling I60a with conduit I60c for dischargevinto the lower end of the right hand cylinder 52' effecting retraction of the front platen and abrading members carried thereby.

The several parts just described having reached their limit of movement under the influence of the coupled pressure 011, the pressure will tend to rise in conduit I60, as a result of which the sequence or delay valve I12 will be operated, permitting oil to flow .into conduit I13. This reacts on valve I14 in chamber I15 moving same to the left.

The speed of valve plunger I14 moving to the left is controlled by the setting of the spring 202a in check valve 202. Three things happen in the following order when the valve plunger I14 moves to the left. First, conduit 20I is disconnected from line 204 which sets up the correct timin conditions for the platens when starting thecycle; second, conduit I16 is disconnected from conduit I22 d which causes the headstock motor 9|, and also the hydraulic motor I39, which drives the oscillator pumps, to stop; third, conduit I13 18 connected to conduit I11 which enters chamber I19 and forces valve plunger I18 to the left. It should be noted at this timethat when valve plunger I14 was moved to the left the oil was discharged on the left end through check valve 202 to conduit 20Ia to conduit 20I through valve 200 to conduit I99 to conduit I98 to conduit I93 to conduit I28 to back pressure relief valve I29 to the reservoir through conduit I28.

When valve I18 moves -to the left the table is stopped because the connection between conduit 206 and conduit I is broken and conduit I90 is connected to conduit I9I to I92 to I93 to I28 to back pressure relief valve I29 to the reservoir through conduit I28. The table stops because both ends of the table cylinder 34 are connected to exhaust pressure.

When valve plunger I18 moves to the left, 011 is discharged from the left end through conduit I99 to conduit I93 to conduit I28 to back pressure relief valve I29 to the reservoir through conduit From the above description it should be understood that by placing the start stop lever I58 in the position shown on Figure 16 that all machine functions are stopped in the following order: 1, The platens are returned, pulling the stones awa; from the work while the headstock is still running and the stones are still reciprocating slowly; 2, The headstock and stones stop moving after the stones have left the work; 3. The table stops.

The machine cycle is started by moving start stop lever I58 in a counterclockwise direction asviewed in Figure 16, initially to bring detent I94 in engagement with notch I 95.

The machine functions start in the following order. First, the table starts to move; second, the headstock starts to rotate slowly, and the stones start to oscillate slowly; third, the platens move the stones into contact with the work; fourth, the speed of the headstock and stone oscillators is increased by moving the start stop lever I58 farther to the left which through link I58 moves start stop valve plunger I51 to the right and opens the throttle between conduit I22d and conduit I22.

When start stop valve is placed in the initial position, as described above, two things happen; first, conduit I53, which is conected to the pump, is, connected to conduit I98; second, conduit I22d is connected to conduit I122 through thethrottled portion of groove I96 in valve plunger I51. The connection of conduit I98 to a pressure source causes valve plunger I18 to move to the right, which causes two things to happen in the following order; first, conduit 206 is connected to line I90 which together with the passageway through the throttle valve 208 and conduit I88 make up the pressure connections which run the table. The table will, therefore, start first. The direction of table movement will depend on the position of the levers 2I3 and 2I I. If the levers point to the left the table will move to the left; if the levers point to the right, the table will move to the right. Lever 2I3 is operated by dogs 2 which are fastened to the table as shown on Figure 1.

Lever 2I I is hand operated and the operator can reverse the table at any time at any position of its stroke. When the levers 2I2 and 2I I' .point to the left the oil supply into the table stopping the cycle.

versing valve I 8| to conduit I80 When thepilot valve 2I I trips by moving to the left, pressure oil is admitted from conduit 20.1;to passage2l5 to I80. Conduit 201 is always connected to pump pressure.

Second, conduit I98 is connected to conduit I99 which together with passageway through selectorvalve 200 and the conduits 20I and 20Ia forms the pressure connection to the left hand end of valve plunger I14 which causes it to move to the right.

It should be noted at this time that when valve plunger I18 is moved to the right that the oil discharged from the right hand side flows to the reservoir through conduit I11 through valve chamber I through conduit I18 through the check valve I12 through valve chamber I59 to conduit I98 through back pressure valve I29 to conduit I28.

The pressure connection now formed at "In causes the valve plunger to move to the right. The valve plunger moves to the right slowly because oil must pass through a restricting groove 202' which bypasses the check valve 202. When the valve plunger I14 moves to the right three things happen in the following order.

First, conduit I18 is connected to conduit I22d which together with the passageway through valve plunger I98 and conduits I22 and I22a form the pressure connections to the head-stock motor 9| and the hydraulic motor I89, which runs the oscillator pumps. The headstock and stone oscillation will start soon after-the table starts. Second, conduit I is connected toconduit 204 through the valve passage 208 in valve plunger I14 whichv forms the pressure connection to the platenaotuating cylinders.

It will be noted that conduit 204 at the rear of the machine is coupled to the outer or, as diagrammatically indicated, lower side of piston 5I. tending to move'the piston upward or in a direction to react on the platen controlling eccentrics, moving the" abrading members carried thereby intoengagement with the rear portion of. the now rotating work. v Atthe same time this pressure reacts through valve I8I to shift the piston 5I for the front platen and similarly move it and its supported abrading members into engagement with the front portion of thework, assuming thatvalve I8I remains in the position shown in the diagram.

It will, of course, be understood that if, for any reason, it is desired that the forward platen shall remain in retracted position with respect to the work, valve I8I may be manually operated as by. control lever 205 to shift the valve from the position shown in Figure 16 to a lower position in which the pressurein 204 will react on the underside of the piston to maintain the parts retracted.

' It should be understood that lever 205 must be moved to the right, and start stop lever I 58 must be'moved to the left simultaneously in order to obtain the above results.

The third thing that happens when valve plunger I14 moves to the right is that the connection between conduit I11 and I13 is broken, thereby setting up correct timing conditions for It should be noted at this time that when the valve plunger I14 moves to the rightthat the oil discharged on the right flows back to the reservoir through conduit I13 through the check valve I12, through the valve passage I59 to conduit I98 through back pressure relief valve I29 to conduit I28,

At this time the function of selector valves 208 and 200 should be explained.

In the position shown on Figure 16 the valve 208 acts as a throttle valve to control the speed of the table movement. If the valve plunger of selector valve 208 is pushed in, the connection between conduit I90 and I88 is broken and the connection between I88 and I89 is made. Therefore, the table will stop, because both ends of the table cylinder 84 are connected to the reservoir, but all other machine functions will continue.

This condition is necessary for. a plunge cut cycle, that is, when the work piece is shorter than the stone and the table traverse is unnecessary.

In the position shown on Figure 16 valve 200 merely acts as a passageway to connect conduit I99 to conduit 20I but if the plunger of valve 200 is moved to the right, not only is the connection between conduit I99 and conduit 20I broken butconduit 20I is connected to conduit I28 which is finally connected to the reservoir. Now, if the start-stop valve I51 is moved to the right or starting position the only thing that will run is the table. The other machin functions cannot start because the pressure connection to valve plunger I14 is blocked.

This valve is necessary for set-up conditions. The operator can line up the stones with that portion of the work piece to be finished without having the work rotate or the stones oscillating and in contact with the work.

At this time thefunction of hand lever 205, valve plunger IN and I82 should be explained. On this machine it is possible to use fine abrasive stones on the rear set of stones for finishing and I coarser abrasive stones on the front for roughing.

At the will of the operator the front set of stones can be removed from the work by moving valve plunger I8I down by means of hand lever 205. This connects conduit 204 with Ic and I80d. Oil pressure in I800 causes the front platen operating cylinder to act and move the front platen which moves the front set of stones away from the work. 011 pressure in I80d moves valve plunger I82 down and this forms a connection be-- tween conduit I88 and I84 and between conduit I85 and I88. Conduits I88 and I84 are connected to two cylinders of the oscillator plunger pump,.the pistons of which are moving in opposite directions and therefore the oil is merely pumped from one cylinder to the other and no oil is supplied to the stone oscillator cylinders. The same is true of conduits I85 and I88. When valve I8I is moved down the' pressure in line 288 is dropped to exhaust pressure and therefore the spring 288,- acting on plunger 222 of the-cutting fluid shut-off valve shown'in Figure 15, moves the plunger to the left and shuts off the cutting fluid supply. It should be understood now that the act of moving lever 205 to the right causes will be advanced to the work at the proper time as explained above.

The function of cylinders I61- -l68--I69l10 is explained as follows. If the work piece being finished is so short that all of the stones are not needed then the oscillation of those not needed cylinder is free to move the stone will not oscillate.

In order that the flow of cutting fluid to the work may be automatically controlled and shut off when the stones are retracted from engagement with the work, use is made of the interconnected hydraulic control mechanism particularly illustrated in Figure 15. The cutting fluid from tank 83 is discharged by pump 84 and conduit. 2I6, blotter filter 2H and conduit M8 to the relief valve mechanism having a first valve device 2I9 controlling discharge into the general supply line 220 branching to the individual shutoif valves 22 I individual to the rear set of flnishing heads, and 222, individual to the front set of I finishing heads. The supply conduits 82 and 82a extend from these shut-off valves to the respective individual heads of the series.

The general relief valve has a second pressure determining valve 223 controlling flow into conduit 224 having branches as at 225 for effecting lubrication of the ways or other desired portions of the machine and an additional branch conduit 226 adaptedto communicate through the series of check valves 22! Figure 16 with the series of conduits 228 individual to the various stone re-' ciprocator motor groups, while the check valves 221 tend to retain the hydraulic actuating fluid in the various oscillator chambers of the stone oscillator motor; in the event of leakage they will yield, permitting the cutting fluid to replenish and keep the system filled. It is to be noted that outwardly opening relief valves 229 have been provided, permitting escape of fluid in the event of undue resistance to operation of the abradant reciprocating motors, and the conduit 226, therefore, also serves to replenish any fluid which may be lost in this manner so that the stone reciprocating system is at all times kept 100% fllled and effective.

To control the opening and closing of the cutting fluid flow control valves HI and 222, they have been provided with the hydraulically actuable plungers 230 and 23!. Plunger 230 is coupled by conduit 232 with the conduit 204 which when under pressure is effective to cause inward or work-engaging movement of the-rear set of work abrading members. Consequently, when actuating pressure exists in this line it will serve to move valve 22l to the right, as viewed in Figure 15, permitting suitable flow of cutting fluid. Conversely, when conduit 204 becomes a reservoir or low pressure conduit, spring 235 is effective to move the valve into closed position. shutting off the flow.

Similarly, plunger 23l is coupled by conduit 233 alternatively with either pressure conduit 204 or conduit I60, depending on the position of the individual control valve I6I for determining the position of platen motor 5| When the valve is in position to eflect inward movement of the front series of work abrading members, pressure will exist in conduit 233, opening valve 222 for flow of cutting fluid, while when the valve is shifted to cause independent retraction of the forward series of tools the flow is automatically shut oil? due to positioning of the valve by expansion of spring 236.

It will be understood that a suitable relief valve, as indicated at 231, may be employed to permit return of excess discharge of pump 84 to reservoir 83 when the valves 22! and 222 are closed.

From the foregoing it will be noted that in the operation of our improved finishing machine, through utilization of the various hydraulic and other control mechanisms shown and described, it is possible satisfactorily to initiate a relative traversing movement of the work and abrading members, to effect an initial slow starting up of the headstock motor with either a power rotative or combined rotation and superimposed movement of rotary oscillation, together with independent reciprocations of the various individual work engaging tools and to bring the moving tools automatically into engagement with the rotating work piece during the relative translation of tools and work piece in such manner that no initial scratching or marking will be produced on the work; and that after the parts have been so operatively related the additional shifting of the startcontrol lever effects a speeding up of the relative work and tool movements for satisfactory performance of the surfacing operation.

At the same time the movement tending to cause interengagement of work and surfacing tools reacts on additional control mechanism to insure proper supply of cutting fluid medium as respects the particular tools being operatively related to the work. Conversely, upon stopping of the machine the cutting fluid flow isautomatically discontinued, the tools retracted as respects the work piece and their reciprocating movement stopped and all relative movement between work and tools ceases.

Additionally, it is to be noted that in the case of a machine employing a multiplicity of tool holders the reciprocation of any individual tool can be checked at will, the tool individually retracted as respects the work, or disengaging pressure upon the work, individually varied as desired without effect on the action of its complementary interconnected opposed tool.

It is further to be noted that the structure in question assures a satisfactory cold cutting of the material being operated upon by providing a constantly changing direction of motion between the abrading elements and the work surface, thus preventing accumulation of chip.material on any active facets of these elements, and thus maintaining a free cutting action. Also, that the particular configuration of path traced by an individual abrasive particle on the surface of the work as a result of the combined relative movements of tool and work may be of either the flgure eight configuration shown in Figure 14 or of overlapping spiral whirls or other forms depending upon the modifications possible in the machine for changing the frequency ratio of the work oscillations and the longitudinal reciprocations of the abrading members, but that in any event the path is of a constantly changing character such that a particular side or facet'on the individual abrasive particle is but momentarily effective when the cut is'transfe'rred to a diflerent angular relation about the periphery of the individual cutting point, tending to free the previously removed bit of metal from the point so that these infinitesimal chips will each be cleanly cut away orremoved without dragging or tearing and be of such minute character as to be readily carried away by the provided cutting fluid flow.

As stated above, the stone oscillator plunger pump and the headstock oscillator plunger pump is shown only diagrammatically in the hydraulic diagram as shown on Figure 16.

By reference to Figure 17 it is evident that the headstock oscillator plunger pump 233 may .be directly connected to the stone oscillator plunger pump 239 by means of coupling I38a and also to the hydraulic motor I33, which drives both pumps, by means of Oldham coupling I33a.

The stone oscillator pump 233 has eight cylinders, the construction of which are identical with those in the headstock oscillator plunger pump 233 as indicated by cylinders I35 and I30, pistons I36 and Ill and springs I32.

' Each cylinder in the stone oscillator plunger pump is connected to one of the stone oscillator The arrangement of the cylinders in the head-.

stock oscillating pump 233 is similar to the arrangement in the stone oscillator pump 239 but for a diflerent reason.

Owing to the large vdisplacement of the headstock motor 9|, thequantityof 011 required is four times the' quantity required to give stone oscillation; Therefore the eight cylinders of this pump are connected inparallel in two groups of four by means of interdrilling in the pump housing in such a manner that they act hydraulically as two opposed pistons and cylinders.

In, order toprovidea path for the abrasive grits relative to the work surface such as shown in Figure 14, the cams I31 on the headstock oscillator pump 233 are each provided with two lobes, while the corresponding cams on the'stone oscillator pump 23 9 are each provided with four lobes, thus the frequency of oscillationsiof the head'- stock will be one-half that of the stone reciprocations. Moreover, the phase relation between headstock motion and stone is such as to produce the desired pattern,'Figure 14. v

III a circular'path, instead of a figure eight, is

desired for the abrasive, four'lobes may also be used onteach'ofthe-cams I31, and the phase relation between headstock motionand stone motion be madeequal to one-fourth of the cycle angle.

If a varying path be desired for the abrasive, the number of lobes on the cam'I3I may be either two or four, and the coupling I331: may be replaced by a gear box arranged to give -a slightly diflerent speed to the pump 239-relative to the pump 2 33.

It should be noted that the symmetrical design of the plunger pumps makes it possible to efl'ecting a progressive rotary advance of the work 4 supplyheavy springs I42 to hold thepistons .against the rollers and the rollers against the camshaft without placing any unbalanced load on the cam shafts. As an extra precaution to insure smooth running of the plunger pumps a flywheel I38b has been added to the rotating system.

A complete dynamic equilibrium of the ma chine may readily be obtained with respect to the reciprocating masses of the stone heads by mak ing the phase relation oftheir motionsuch that each pair of diametrically opposed stones, and each pair of adjacent stones are out of phase with each other. This provides a complete balance in the axial forcespn the work and insures a steady and quietly operating machine.

What is claimed is:

1. A machine of the character described including a work support, means for supporting an abrading tool in opposition to a work piece carried by the support, a tool reciprocably mounted on said supporting means, means for effecting high speed reciprocation of said tool, means for effecting a progressive rotary advance of the work with respect to the tool and a simultaneous relative traverse of said parts, a hydraulic actuator, conduits coupling said actuator with said several means for eifecting the operation thereof, said means for eifecting' the progressive rotary advance of the article including a hydraulic motor, a conduit for supplying actuating medium unidirectionally thereto at a predetermined rate, and additional means for effecting alternating pulsations in the motor supply fluid whereby a combined rotational advance and pulsating means for effecting the operation thereof, said means for effecting the progressive rotaryadvance oi the article including a hydraulic motor, a conduit for supplying actuating medium unidirectionally thereto at a predetermined rate, ad.-

ditional means for eflecting alternating pulsations in the motor supply fluid whereby a combined. rotational advance and pulsating movements of rotary. oscillation are imparted to the motor, and .means for coupling the actuating medium to the motor inclusive or exclusive of said pulsator. I v

3. A machine of thecharacter, described including a work support, means for supporting an abrading tool in opposition to a work piece carried by thesupport, a tool reciprocably mounted on said supporting means, means for effecting high speed reciprocation of said tool, means for with respect .to the tool and a simultaneous relative traverse of said parts, a hydraulic actuator, conduits coupling said actuator with said severalmeans for effecting the operation thereof, said means for effecting the progressive rota y advance of the article including a hydraulic motor, a conduit for supplying actuating medium unidirectionally thereto 'at' a predetermined rate, additional means for effecting alternating pulsations in the motor supply fluid whereby a com bined rotational advance and pulsating movements of rotary oscillation are imparted to the motor, means for coupling the actuating medium to the motor inclusive or exclusive of said pulsator, an additional controller for determining the operative connection or disconnection of the hydraulic actuator with the hydraulic motor, and means actuable by said additional controller for determining the effective positioning of the tool holding means with respect to the motor actuated work piece.

4. A finishing machine of the character described, including a bed, headstock and tailstock members intermediately mounted on the bed for support of a work piece therebetween, tool supporting carriages mounted on the bedon opposite sides of the potential work position, means for determining the joint or individual movement of the tool supports toward and from the work position, means for efiecting a back and forth translation of the work supports on the bed, individual tool holders carried by the tool supports, means for individually effecting ,vibratory reciprocations of the individual tool supports, a hydraulic headstock motor, means for porting carriages mounted on the bed on opposite sides of the potential work position, means for determining the joint or individual movement of the tool supports toward and from the work position, means for effecting a back and forth translation of the work supports on the bed, individual tool holders carried by the tool supports, means for individually eifecting vibratory reciprocations of the individual tool supports, -a hydraulic headstock motor, means for supplying actuating fluid to the headstock motor at a predetermined rate-for effecting rotation of the headstock and thus of a supported work piece with respect to the vibrating tool supports, additional means for producing alternating vibratory pulsations in the fluid supply to the headstock motor whereby a rotary oscillatory-movement is superimposed on the primary rotary movement of the headstock, said means for effecting vibration of the tool holders comprising hydraulic motors individual to the respective tool holders, a hydraulic circuit including the motors, and means for creating alternating pulsations in said circuit for actuation of the motors, substantially as and for the purpose described.

6. A finishing machine of the character described, including a bed, headstock and tailstock members intermediately mounted on the bed for support of a work piece therebetween, .tool supporting carriages mounted on the bed on opposite sides of the potential work position, means for determining the joint or individual movement of the tool supports toward and from the work position, means for efiecting a back and forth translation of the work supports on the bed, individual tool holders carried by the tool supports, means for individually effecting vibratory reciprocations of the individual tool supports, a hydraulic headstock motor, means for supplying actuating fluid to the headstock motor at a predetermined rate for efiecting rotation of the headstock and thus of a supported work piece with respect to the vibrating tool supports, additional means for producing alternating vibratory pulsations in the fluid supply to the headstock motor whereby a rotary oscillatory movement is superimposed on the primary rotary movement of the headstock, said means for effecting vibration of the tool holders comprising hydraulic motors individual to the respective tool holders, a hydraulic circuit including the motors, means for creating alternating pulsations in said circuit for actuation of the motors, and a constantly driven member having individual elements for producing the tool and the headstock motor pulsations, substantially as and for the purpose described.

7. A finishing machine of the character described, including a bed, headstock and tailstock members intermediately mounted on the bed for support of a work piece therebetween, tool supporting carriages mounted on the bed on opposite sides of the potential work position, means for determining the joint or individual movement of the tool supports toward and from the work position, means for effecting a back and forth translation of the work supports on the bed, individual tool holders carried by the tool supports, means for individually efiecting vibratory reciprocations of the individual tool supports, a hydraulic headstock motor, means for supplying actuating fluid to the headstock motor at a predetermined rate for efiecting rotation of the headstock and thus of a supported work piece with respect to the vibrating tool supports, additional means for producing alternating vibratory pulsations in the fluid supply to the headstock motor whereby a rotary oscillatory movement is superimposed on the primary rotary movement of the headstock, said means for efiecting vibration of the tool holders comprising hydraulic motors individual to the respective tool holders, a hydraulic circuit including the motors, means for creating alternating pulsations in said circuit for actuation of the motors, a constantly driven member having individual elements for producing the tool and" the headstock motor pulsations, and a single control member for simultaneously determining the actuation of the several hydraulically operated members.

8. A finishing machine of the character described, including a bed, headstock and ta lstock members intermediately mounted on the bed for support of a Work piece therebetween, tool supporting carriages mounted on the bed on opposite sides of the potential work position, means for determining the joint or individual movement of the tool supports toward and from the work position, means for effecting a back and forth translation of the work supports on the bed, individual tool holders carried by the tool supports, means for individually effecting vibratory reciprocations of the individual tool supports, a hydraulic headstock motor, means for supplying actuating fluid to the headstock motor at a predetermined rate for efiecting rotation 01' the headstock and thus of a supported work piece with respect to the vibrating tool supports, additional means for producing alternating vibratory pulsations in the fluid supply to the headstock motor whereby a rotary oscillatory movement is superimposed on the primary rotary movement of the headstock, said means for effecting vibration of the tool holders comprising hydraulic motors individual to the respective tool holders, a hydraulic circuit including the motors, means for creating alternating pulsations in said circuit for actuation of the motors, a constantly driven member having individual elements for producing the tool and the headstock motor pulsations, 3. single control member for simultaneously determining the actuation of the several hydraulically operated members, and a selector device for determination of the reaction eifect of the headstock motor pulsator on said motor.

9. A finishing-machine of the character described, including a bed, headstock and tailstock members intermediately mounted on the bed for support of a work piece therebetween, tool supporting carriages mounted on the, bed on opposite sides of the potential work position, means for determining the joint or-individual movement of th tool supports toward and from the work position, means .for effecting a back and forth translation of the work supports on the bed, individual tool holders carried by the tool supports, means for individually efiecting vibratory reciprocations or the individual tool supports, a hydraulic headstock motor, means for supplying actuating fluid to the headstock motor at a predetermined rate for eflecting rotation of the headstock and thus of a supported work piece 7 with respect to the vibrating tool supports, additional means for producing alternating vibratory pulsations in the fluid supply to the headstock holders.

10, A finishing machine of the character described, including a bed, headstock and tailstock members intermediately mounted on the bed for 7 pulsator devices as respects the individual tool support of a work piece therebetween, tool supporting carriages mounted on the bed on opposite sides of the potential work position, means for determining the joint or individual movement of the tool supports toward and from the work position, means for effecting a back and forth translation of the work supports on the bed, individual tool holders carried by the tool supports, means for individually effecting vibratory reciprocations of the individual tool supports, a hydraulic headstock motor, means for supplying actuating fluid to the headstock motor at a predetermined rate for effecting rotation of the headstock and thus of a'supported work piece with respect to the vibrating tool supports, addi-' tional means for producing alternating vibratory pulsations in the fiuid'supply to the headstock motor ,whereby a rotary oscillatory movement is superimposed on the primary rotary movement of the headstock. said means for effecting vibration of the tool holders comprising hydraulic motors individual to. the respective tool holders, a hydraulic circuit including the motors, means for creating alternating pulsations in said cir- V-cuit for actuation of the motors, a constantly driven member having individual elements ior producing the tool andthe headstock motor pulsations, a single control member for simultaneously determining the actuation of the several hydraulically operated members, and individual selector devices for determining the reaction effect oi the pulsator means on the headstock motor and on the tool holders.

11. A finishing machine of the character described, including a work support, a tool carrying platen, means for moving the platen in the direction 01.. the work support for engagement with a work piececarried thereby, a tool support mounted on the platen, a reciprocable tool carried by the support, means for effecting reciprocation oi' the tool, means for eil'ecting a relative translation of the support and platen to produce a traversing movement between the work and tool, a first mechanism for imparting a rotary movement to the work support, a second mechanism for concomitantly eifecting a pulsating oscillation of rotary type or the work support during its rotation, a hydraulic control circuit for the several work and tool shifting members including multiple successively shiftable valve elements, and a control for said hydraulic circuit actuable to effect relative traverse of the tool platen and work support and relative approach movement and simultaneously eifect initial slow and subsequent accelerated movements of the work and tool driving elements,

12. A finishing machine of the characterv described, including a work support, a tool carrying platen, means for moving the platen in the direction of the work support for engagement with a work piece carried thereby, a tool support mounted on the platen, a reciprocable tool carried by the support, means for effecting reciprocation of the tool, means for effecting a relative I translation of the support and platen to produce a traversing movement between the work and tool, a first mechanism for imparting a rotary movement to the work support, 'a second mechanism for concomitantly effecting a pulsating oscillation oi rotary type ofthe work support during its rotation, a hydraulic control circuit for the several work and tool shifting members,

including multiple successively shii'table valve elements, a control for said hydraulic circuit actuable to eifect relative traverse of the tool platen and work support and relative approach movement and simultaneously 'eflect initial slow and subsequent accelerated movements of the work and tool driving elements, and additional control means forvariably determining the the ratio of rotary and pulsating movements of rotary work support.

13. A finishing machine of the character described, including a work support, a tool carrying platen, means for moving the platen in the direc'tim of the work support i'or. engagement with a work piece carried thereby, a tool support mounted onthe platen, a reclprocable tool carried by the support, means for electing reciproe cation of the tool, means for eifecting a relative translation of the support and platen to produce a traversing movement between the work and tool, a flrst'mechanism for imparting a rotary movement to the tool support, a second mechanism for concomitantly eifecting a pulsating I oscillation of rotary type of. the work support during its rotation, a hydraulic control circuit for the several work and .tool shifting members including multiple successively shiitable' valve elements, a control for said hydraulic circuit actuable to eflect relativetraverse of the tool platen and work support and relative approach movement and simultaneously effect initial slow and subsequent accelerated movements of the work and tool driving elements, and selector means for determining the eflective reaction of the hydraulic circuit on the work rotating and tool reciprocating elements.

14. A machine of the character described including a bed, a work support mounted thereon,

a hydraulic motor for eflecting rotation oi the work support, tool supports carried by. the bed having tool portions for operative engagement with a work piece held by the rotary support, and means for effecting actuation oi the parts including a first hydraulic circuit for effecting rotation of the hydraulic motor, a second hydraulic circuit including a motor and a plurality of pulsators driven thereby, an operative connection between one of the pulsators and the hydraulic motor for eflecting alternatingpulsations of rotary oscillation of the motor supplementing the hydraulic rotation thereof eflectable .by the first-mentioned circuit.

15. A machine oi the character described including a bed, a work support mounted thereon,

a hydraulic motor for effecting rotation of the work support, tool supporm carried by the bed having tool portions for operative engagement with a workpiece held by the rotary support,

means for effecting actuation oi the parts in-.

cluding a first hydraulic circuit for eflfecting rotation of the hydraulic motor, a second hydraulic circuit including a motor and a plurality of pulsators driven thereby, an operative connection between one of the pulsators and the hydraulic motor for vefiecting altdrnating pulsations oi rotary oscillation of the motor supplementing the;

hydraulic rotation thereof efiectable bythe firstmentioned circuit, reciprocable hydraulic motors individual to the respective tools, and hydraulic connections between theother pulsatorsand said motors-for determining theindividual reciprocations of the tools. p v

16. A machine or the character described'ineluding a bed, a work support mounted thereon,-

a hydraulic motor for effecting rotation o; the work support, tool supports carried by the bed having tool portions for operative engagement with a work-piece held by the rotary support, means ior effecting actuation of the parts including' a first hydraulic circuit for eflecting rotation of the hydraulic motor, a second hydraulic circuit including'a motor anda plurality of pulsators' driven thereby, an operative connection. between one or the vpulsators and the hydraulic motor for eflecting alternating pulsations oi ro-f tary oscillation of the motor supplementing the hydraulic rotation thereof efiectable by the firstmentioned circuit, reciprocable hydraulic motors individual to the respective tools, hydraulic connections between the other pulsators andsaid motors for determining the individual reciprocations of the tools, and controllable means coupled with said connections for absorbing the pulsations to prevent reciprocation-of the tools.

17. In a machine of the character described,

the combination with a bed, a work support mounted thereon, of tool carrying platens disposed at opposite sides or the support, tools carcorresponding movements of the platens with respect to the work support.

- 18. In a machine the character described,

the combination with a. bed, a work supportmounted thereon, of tool carrying platens disposed at opposite sides of the support, tools carried thereby for engagement with a work piece,

, individual hydraulic motors for controlling the position of the tool platens with respect to the work support, control means for effecting. jointor individual actuation of the motors for corresponding movements of the platens with respect to the work support, means for supplying cutting fluid to the tools, flow control valves individual to the respective.platens,.and hydraulic connections intervening the platen shifting motors and said valves for eflectingopeningand closing '0! the valves in prescribedrelation to the positioning o'i'the platens.

19. In a machine of the character described, includinga rotatably mounted work support, a

tool support means for effecting relative translation oi said supports, and means for impartingrotational movement to the work support, of hydraulic actuatingmeans for the parts, and

m'eans'for' controlling the power reaction of the hydraulic actuating means on the parts including a starting valve, serially'arranged pilot andselector valves for determining the coupling oi! guides having an actuating projection to one side thereof, a piston member engagedon said projectlon, a chamber formed in the head and receiving said piston, opposed springs contained within the chamber oppositely reacting on the piston, and means ioreifec'ting hydraulic power 1 ried thereby for engagement with a workpiece, individual hydraulic motors for controlling the position of the tool platens with respect to the work support, and control means for eii'ecting joint or individual actuation oi the'motors for pulsations in one end of the chamber for effecting successive compressions oi the opposed piston engaging spring, whereby ultimate-movement of I the piston in both directions will be absorbed by the respective sprin and' a smooth high speed reciprocation imparted to the tool holder,

" substantially as and for the purpose described.

21. A machine oithe character described, including' work and tool supporting means, means to eflect a relative traverse of said parts, means to effect independent-reciprocation of the tool,

means to eflect rotation oi the work, and a'single control device having a first position effective to initiate said relative traverse reciprocation and work rotation movements and to bring the tool and work into operative engagement one with the other, and a second position for effecting a speeding up of certain of said movements subsequentto said relative engagement of the parts.

22. A machine of the character described, in-

cluding work and tool supporting means, means to eiIect a relative traverse of said parts, means to effect independent reciprocation of the tool,

means to effect rotation of the work, and a single control device having a first position effective to initiate said relative traverse reciprocation and work rotation movements and to bring the

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