US2078696A - Hydraulic material working apparatus - Google Patents

Description

April 3937 E. J. SVENSON HYDRAULIC MATERIAL WORKING APPARATUS Original Filed Spt. 15, 1930- e Sheets-Sheet 1 April 27, 1937. E. J. SVENSON HYDRAULIC MATERIAL WORKING APPARATUS Original Filed Sept. 15, 1930 6 Sheets-Sheet 2 April 27, 1937.

E. J. SVENSON HYDRAULIC MATERIAL WORKING APPARATUS Original Filed Sept. 13, 1930 6 Sheets-Sheet 3 I! I a.

m www April 27, 19374 E. J. SVENSON HYDRAULIC MATERIAL WORKING APPARATUS Original Filed Sept. 13, 1930 6 Sheets-Sheet 4 6 M2 n 5. 8 Q o g 0 E w m g 0 2 7. z 3 m III 3 P u w u W Z %Hw Q .7 m @1 0 J N6 4 2 Q E, Q 020 MW? 0 v W J Y 9 l k 5 A w a 4 0 J 64 6 22 1 m4 55% I E. J. SVENSON HYDRAULIC MATERIAL WORKING APPARATUS A April 27, 1937.

e Sheets-Sheet 6 Original Filed Sept. 13, 1930 l l l I l I I NNM m www wNw UNlTED ST-ATES PATENT OFFICE HYDRAULIC MATERIAL WORKING APPARATUS Ernest J. Svenson, Rockford, Ill.

Application September 13, 1930, Serial No. 481,142 Renewed February, 3, 1937 10:; Claims. (c1. n 2) My invention. relates generally to hydraulic rect fluid from a'suitable source of supply to material working apparatus, and'more particuthe hydraulic mechanism which controls the larly to apparatus such as automatic lathes andactuation of a second hydraulic mechanism, and the like which are equipped with hydraulic 5315- in another shifted position serves to direct fluid tems of control. for rapid traverse purposes to both of said hy- 5 In using conventional types of material workdraulic mechanisms. In other words, my invening apparatus, such as automaticlathes having. tion contemplates the provision of a system of a plurality of movable tool carriages, considercontrol for a plurality of hydraulic actuators, able diificulty has been experienced in controlling in which a valve serves to initially direct fluid the mov m n f tOOlS- Thi f t is particularly to one of the actuators only, and subsequently 10 true in connection With the ydraulic control of to direct fluid to all of the actuators in order to a plurality of carriages. In other words, it has efiect rapid reversetraverse of said actuators. been found difiicult to control the movements of Another object of my present invention is to a plurality of machine carriages so that each provide, in combination with the hydraulic syscarriage is moved to a predetermined position tem of contr l ab v set forth, a plurality of lit wi h r p to the other carriage or carriages closed hydraulic circuits, whereby feeding moveduring a predetermined interval of time. ment is imparted to the actuators.

It is one of the primary objects of my present In addition to providing improved hydraulic invention to overcome difficulties heretofore exircuits, my invention contemplates the pro- Derienoed y P v in ehydmulie System Of 0011- vision of improved mechanical control devices, 20 trol which will serve to accurately and positively whereby th shifting of carriages, such as the p i i ne rriage with respect to another front and rear carriages of a lathe, may be etduring each successive cycle of operation of the fectively governed, machine. The foregoing and numerous other objects and More specifically, it ght be S at d that my advantages will be more apparent from the fol- 25 inv n i n n p ates the provi i n f a new lowing detailed description when considered in and improved hydraulic system of control which connection th th accompanying drawings,' is so arranged that a plurality of shiftable tools, wherein F as for example, tools on front and rear carriages Figure 1 1 plan View of an automatic b of an auto c lathe. y he brought into draulically controlled lathe which is constructed 30 gag'ement with a rotating W r piece at a P p in accordance with'the teachings of my present predetermined time during each successive cycle invention; of operation of the machine. 7 Figure 2 is an enlarged plan view 01' the dog Another obj f my p n invention i to carrying slide and associated valve mechanisms, provide in a hydraulic system of control as a r m f said structure being shown in section 35 above Set forth, a singledcontml means P in order to more clearly set forth the general artremely simple and practical construction, whererangement e by the movements of the hydraulically operated Figure 3 forms a continuation of Figure 2 and machine parts may be conveniently controlled. discloses fragmentaruy the portion. of the rear 40 In order to bring about the above mentioned 11d ewed alon the une 40 accurate control of the movements of a plurality gg ggg fi S e as! w g machine camagesor the I propose to so Figure 4 is a fragmentary vertical sectional arrange the hydraulic system of control that the hydraulic mechanism Shifting one carriage view taken longitudinally of .the slide substan is controlled directly by the mechanism which along the line of a f th 45 hydraulically actuates another carriage. In Figure 5 is transverse-M10113 .3 1 8 other words-1 propose to operate one of Said rotary control valve for the front ca age 0 rhydraulic mechanisms directly in ggspcnse t cult, said view being taken substantially along the actuation of another carriage operating the line 5 E ha i Figure 6 is a transverse vertical sectional view 50 A still further object or my present invention of the control valve and the associated P rtion is to provide, in combination with the hydraulic of the dog carrying slide, said view being taken system of control just set forth, an improved substantially along the line 6-8 of Figure 2; control valvev of extremely simple construction, Figure 7 is a transverse-vertical sectional view '55 said valve in one shifted position serving to ditaken along the'line 1-4 of Figure 8; 5 5

Figure 8 is a horizontal sectional view taken substantially along the line 8--8 of Figure '7;

Figure 9 is a transverse sectional view of the control valve taken substantially along the line 9-9 of Figure 8;

Figure 10 is a similar transverse sectional view taken along the line Ill-l0 of Figure 8;

Figure 11 is a fragmentary detail sectional view of the unbalancing mechanism, said mechanism being shown in position to unbalance the fluid pressure within the chambers of the valve mechanism shown in Figure 8;

Figure 12 is a transverse vertical sectional View of one of the variable displacement, high pressure plunger pumps which is employed for feeding purposes, said .view being taken substantially along the line I 2|2 of Figure l;

Figure 13 is a transverse vertical sectional view of said pump taken substantially along-the line I3l3 of Figure 12;

Figure 14 is a fragmentary end elevational view of the automatic lathe as viewed from the left end of Figure 1;

Figure 15 is a central transverse sectional view of the check valve which is employed in the low pressure fluid circuit;

Figure 16 is a circuit diagram of my improved hydraulic system of control, said system including the double control valve structure shown in Figures 6 to 10 inclusive, said valve being shown in neutral position;

Figure 1'7 is a sectional view of the valve I mechanism similar to the section shown in Figure 16, disclosing the rapid approach position of said valve mechanism;

Figure 18 is a similar view disclosing the reverse rapid traverse position of said valve mechamsm;

Figure 19 is a transverse sectional view similar to Figure 6, of a modified control valve;

Figure 20 is a horizontal sectional view taken substantially along the line 202ll of Figure 21;

' Figure 21 is a vertical section of the control valve taken substantially along the line 2|2l of Figure 20;

Figure 22 is a transverse section of the valve mechanism taken substantially along the line 22- 22 of Figure 21;

Figure 23 is a similar transverse vertical sectional view taken along the line 23-23 of Figure 21;

Figure 24 is also a transverse sectional view I taken along the line 24--24 of Figure 21; and

Figure 25 discloses a shifted position of the ,unbalancing device of Figure 20.

Referring now to the drawings more in detail, it will be observed that like numerals have been employed to designate similar parts throughout the various figures.

For the purpose of disclosing one practical application of my hydraulic system of control, I have selected an automatic lathe, which is clearly shown in plan in Figure 1.

This lathe is structurally similar in many respects to the lathe which is described and claimed in myco-pending applications, Serial No. 391,130, filed September 9, 1929, and Serial No. 439,306, filed March 27, 1930, and therefore a detailed description of the various elements which constitute the lathe'structure proper is not essential to a complete understanding of the present invention.

However, enough of the structures of the lathe elements are disclosed in the present application -to enable a clear understanding of the co'mbina;

tion thereof with my improved hydraulic system of control so as to clearly set forth at least one practical application of my invention. In order to more readily understand my present invention I shall first proceed to briefly designate certain structures of the lathe, and subsequently describe these structures in connection with my improved mechanism for controlling the operation of these lathe elements.

Referring to Figures 1 and 14, it will be seen that I have disclosed an automatic lathe which includes a suitable base or bed 30, which supports a head stock designated generally by the numeral 32, and a tail stock which is designated generally by the numeral 34. Mounted within this head stock 32 is a suitable work spindle 36, and this spindle 36 is connected with and driven from a clutch mechanism 38. This clutch mechanism 38 serves to connect and disconnect the spindle 36 with a suitable source of power supply, for example, with an electric motor 40 shown in Figure 14. This electric motor 40 is. connected with a rear drive shaft .42 through the agency of a suitable chain belt 44. Thus, the

motor 40 may be continuously operated so as to rotate the drive shaft 42 and when it is desirable, power from the drive shaft 42 is imparted to the spindle 36 by manipulating the clutch mechanism 38. I

Mounted upon the front side of the lathe is a tool carriage which I have designated generally by the numeral 46. This carriage 46 is clamped at its lower end upon a cylindrical bar 48 and is capable of being oscillated with the bar 48 about the axis thereof toward and away from a work piece (not shown), which work piece -is adapted to be supported between the tail stock 34 and a face plate 36a of the spindle 36. This front carriage 46 includes an upper slide 50 which is adjustable toward and away from the workpiece by means of a suitable screw 52, and

this slide supports a suitable tool 54. The oscillat-ion of the carriage 46 with the support bar 48 is controlled by means of a'hydraulic mechanism or actuator which Ihave designated generally by the numeral 56 in Figure 16. This actuator 56 is positioned immediately beneath the outer end of the carriage 46, and includes a cylinder 58 which reciprocably supports'a piston '60. This piston is vertically reciprocablewithin the cylinder 58 and is mounted upon a suitable piston rod 62 which extends on both sides of said piston.

The upper extremity of the piston rod 62 supports the free extremity of a guide bar 64 which is pivotally mounted at 66 on the front side of the machine in any suitable manner. The upper surface of the guide bar 64 serves as a rest for the outer portion of the oscillatory front carriage 46, as shown fragmentarily in Figure 16. Obviously, when the piston 62 experiences an upward movement, the carriage 46 will be swung with the support bar 48 so as to carry the tool 54 into operative association with the work piece.

Longitudinal movement of the tool 54 'and' the carriage 46, upon which it is mounted, is occasioned in response to the actuation of a hydraulic mechanism or actuator 66-, Figures 1 and 16. This actuator 68 includes a cylinder 10 and a piston 12 which is horizontally reciprocable above, carwork-piece. The slide 18 also supports a tool 82, and by means of a suitable screw 84, Figure 1, the slide 18 may beadjusted toward and away from'the work piece. This carriage 16 is arranged to move said tool transversely of the work piece. Movement. is imparted to the slide 18 .through the agency of a suitable hydraulic mechanism or actuator which is designated generally by the numeral 86. ,This actuator includes a cylinder 88 and a piston 90, which is horizontally reciprocable within said cylinder. A pistonrod 92 is provided for the purpose of connecting the piston with the slide 18. Thus, it will be apparent that the actuator 56 controls the 0s.- cillation of the front tool carriage, while the actuator 68 controls the longitudinal movement of said front carriage, and the actuator 86 controls the transverse reciprocation of the rear too carriage 16.

Pumps Mounted upon the upper portion of the head stock 32 is .a pair of fluid propelling mechanisms or pumps 94 and 9411. These pumps are identical in structure and the pump mechanisms per se do not form a part of the present invention, except as said elements enter into the general combination of my improved hydraulic system of control.

Referring to Figures 12 to 14 inclusive, it will be seen that each of these pumps includes a central casing 96, an end casing member 98 on one side thereof, and a second casing section I00 secured to the opposite side of the central casing 96- This casing section I00 provides a support for a plurality of radial pistons I02, and movement is imparted to these pistons through the agency of a driving ring or annulus I04. This I driving ring I08 is mounted on anti-friction bearings supported by a rotatable driving member I06, and this driving member is driven by and laterally adjustable within a sleeve member I08. Keyed to this sleeve member I08 is an annular sprocket H8, connected by means of a chain I I2 with a companion sprocket H4, Figure 14, which is mounted upon the work spindle 36.

'I'hus it will be apparent that the pumps 84 and 84a are driven directly-from the work spindle of the lathe. 3

The driving ring I04 of each of the high pressure plunger pumps may be laterally adjusted by turning an adjusting nut II6. This nut isconnected with a cylindrical member II8 which is provided with an angularly disposed projection I20 which extends into a companion opening in the driving member I06. Thus, by rotating the nut II6, the eccentricity of the driving ring I04 may be varied. The casing section I 00 also serves to support a tapered rotary valve I22 which is adapted to control the flowof fluid toward and away from the outer ends of the pistons I02. Fluid is directed into the pump through a pipe I24which communicates with a chamber I26, and from this chamber fluid passes through a valve passage I28 to a peripheral valve port I30. This valve port I30 "successively registers with radial passageways I32 which communicate at their outer-extremities with chambers I34 at the outer ends of the pistons I02. Fluid is withdrawn during the compression stroke of the pistons through passageways I 32 which register with a peripheral valve port I36. This port communicates with a pipe line I38 through the agency of a valve passage I40. The tapered valve I22 is secured against longitudinal displacement to the right, Figure 12, by means of an antifriction thrust bearing I42 and an abutment screw I44. This tapered valve I22 positively prevents leakage of fluid to the left along the surface thereof, and thus renders the pump particularly adaptable for use in connection with closed fluid circuits. In other words, the pipe lines I24 and I38 form two sides of a closed circuit, about to be described. These pumps 84a, and 94 respectively are adapted to supply fluid at high pressure to the actuator 68, which longitudinally moves the front tool carriage, and to the actuator 86 which moves the rear tool carriage transversely of the work piece.

' A reservoir I46 positioned at the upper portion of the machine contains a supply of fluid, and fluid from this reservoir is directed through a pipe line I48 to the intake side of a gear pump I50. Fluid from the discharge side of the gear pump I50 is directed through a pipe line I52 to the intake port I54 of a valve mechanism which I have designated generally by the numeral I56. This gear pump I 50 is constantly driven from the shaft 42, asclearly shown in Figure 14, and provides the means for supplying low pressure fluid at increased displacement to the actuators for the purpose of imparting rapid movement thereto.-

. Control valve I shall now proceed to describe the valve mechanism I56, and in order that the operation of this valve mechanism may be more readily understood, 1 shall describe the same in connection with the fluid circuit which includes the actuators 66, 68, and 86. This valve mechanism I56, as clearly shown in Figures 1 and 2 and Figures 6 to 11 inclusive, is mounted upon the front side of the machine and is located in a convenient position for manual manipulation by the machine operator. Manual manipulation of this valve is controlled through the agency of a control handle I58, and this control handle serves to reciprocate valve members I60 and I62 which are movable within a casing I64. The valve members I60 and I62 are also adapted to be automatically shifted within the casing and this automatic control will be later described. One end of the casing I64 is closed by a. cover plate I66 and the opposite end is closed by a cover plate I66. This cover plate I68 is provided with a boss I10 which serves as means for supporting a balancing mechanism I12, which will be described later.

to their respective sleeves by means of suitable.

pins I80. The control handle or lever I58 is secured to the outer end of the sleeve I16a by means of a pin I82, and the outer extremity of the sleeve I14a. supports a block I84, which is formed with a pair of dog engaging fingers I86 and I88. These fingers cooperate with mechanisms later to be described, for automatically controlling the shifting of the valve members.

A nut I90 carried at the outer extremityof the shaft H8 is adapted, when tightened in position, to urge the sleeves I'I4a and H642. into firm abutment, and thus bind said sleeves and shaft together as a unit. When these sleeves and shaft are thus secured, movement of the single control handle I58 will cause the simultaneous actuation of both of the valves I 60 and I62. If it is de-, sirable to manually operate one of the valves 10 independently of the other, it is only necessary to loosen. the nut I90. It will be noted that the block I84 is provided with a knurled upwardly extending handle I84a, which serves as a convenient means for manually manipulating said block.

In Figures 6 to 8 inclusive, as well as Figure-16, I have shown the valves I60 and I62 in their. neutral position. When these valves occupy this neutral position, it 'will be observed, by referring particularly to Figures 8 and 16, that fluid from the low pressure pipe line I52 will pass through the intake port I54 of the valve casing, and thence into a passageway I92, and it will be seen by referringto Figure 9 that this passageway I92 extends from one side of the valve casing to the other, or, in other words, encircles both of the valves I60 and I62. In this neutral position of the valve members, the passageway I92 com municates with radial ports I94 in the valve I60 and similar ports I96 in the valve I62. The ports I94 communicatewith a central longitudinal valve passage I98 which opens into an end chamber 200, while the radial ports I96 communicate with a similar longitudinal passage 202 which opens into a chamber 264. These chambers 200 and 204 are connected to a pipe line 206, and them)- per end of this pipe line is connected to-a mecha' nism 208 having an adjustable restricted orifice. Fluid passes through this restricted orifice and is thus returned to the reservoir I46. Thus, it will be apparent that, when. the valve members occupy their neutral position, fluid from the'low pressure source of supply will circulate therethrough and will not be distributed through any of the ports 2 I0, 2I2, 2, and 2 I6 provided within the valve casing I64. It will be noted that the ports 2") and 2I2 are closed by the valve sections 2I8 and 220 respectively, while the ports 2I4 and 2I6 are closed by valve sections 222 and 224 respectively.

Consider now that the valve members are shifted to the position shown in Figure 1'7, which will hereinafter be referred to as the rapid approach position. In this position low pressure fluid from the pipe line I52 passes through the valve port I54 and intothe passageway I92, as' previously described. However, when the valves occupy this shifted position, the radial ports I94 and I96 thereof are closed, thereby preventing the circulation of incoming fluid through the longi tudinal passageways I98 and 202 back to the reservoir I46. The incoming'fluid, however, is directed througha lateral port226 in the valve member I62 to the port 2I4, and from this port the'flui d is conducted through a, suitable conduit or pipe 228 to the lower extremity of the cylinder 58 of the actuator 56. It is to be noted that, when the valve members occupy this rapid approach position, the section 2| 8 of the valve member I60 closes the port 2"), thereby preventing the low pressure fluid from passing outwardly through said port. In other words; when the valve members occupy the positionsho'wn in Figure 17,.fiuid is directed by the valve through a single outlet port, namely, the port 2 I 4 and thence through the pipe line 228.

Fluid entering the cylinder 58 causes the pistion 60 to move upwardly, thereby effecting the swinging of the front tool carriage 46 and its supported tool. 54 toward the work piece. Fluid from the advancing side of the piston 60 passes out of the upper end of the cylinder 58, Figure 16, through a pipe 230, and this pipe connects with one end of a check valve 232 of improved practical construction, which will be described later in detail. It will suffice to say that this valve 232 prevents the reversal of fluid flow into the pipe 230. The other end of the check valve 232 connects with a pipe 234, and this pipe is connected to one extremity of acylinder 236 of a hydraulic clutch operating mechanism, which I have designated generally bythe numeral 238. Fluid entering the cylinder 236 from the pipe 234 passes out wardly through a pipe 240, which connects with one extremity of the cylinder 88. Thus forward 'movement is imparted to the piston 90 in the cylinder 88 in response tothe upward movement of the piston 60. In this manner I am able to piston 60. Fluid from the advancing side of the I piston 90 passes outwardly through a pipe'242 which connects with the valve port 2I2. At this time the valve port 2I2 communicates with an annular port or passage 244 of the valve member I60, Figure 17, and this port 244 communicates with a passageway 246, Figure 7, provided within the valve casing I64. This passageway 246 opens at its opposite extremity into the chambers 200 and 204; and thereby the fluid is returned through the pipe 206 to the reservoir I46.

At this point it should be noted in Figure 16 that the left end of the cylinder 236 of the hydraulic clutch control mechanism 238 is connected to thepipe 242 by means of a pipe-248. Thus, when the valve members are initially shifted to their rapid approach position shown in Figure 17, a piston 250 within the actuator cylinder 236 will be urged to the left, and fluid from the advancing side of this piston will be returned through the pipe 248. The piston 250 through its piston rod 252is-connected with the clutch mechanism 38 as shown; in Figure 1, 'and the movement of this pistonto the left will actuate said clutch mechanism so as to establish a driving connection between the work spindle 36 and the drive shaft 42.

This causes the pumps 94 and 94a to be actuated.

Fluid from the discharge side of the pump 94, Figure 16, passes through the pipe I38, which connects with the outer end of the rear carriage intake side of the pump 94 with the opposite extremity of the cylinder 88; The discharge side of the pump'94a is connected through a pipe 258 with the right end of the cylinder I0 of the actua- 'tor,68. The opposite end of the cylinder I0 is cylinder 88. The return pipe I24 connects the nect the lower end of said cylinder with the pipe 258.

'- From the foregoing it will be understood that when the valves I60 and I62 are simultaneously shifted from the neutral position shown in Figme 16 to the position shown in Figure 17, theactuators 56 and 86 will be operated so as to 'cause; the rapid approach of the fronttool. 54

of the rear tool carriage is effected by the rapid approach of the'front carriage actuator. By having the proper relationship in size of the bores in the cylinders 58 and 88, any predetermined movement of the piston 88 may be obtained by a corresponding movement of the piston 68. In other words, if the cylinder bores are equal in size, the movement imparted to the piston 98 will be equal to .the movement :experienced by the piston 68. However, if the cylinder bore 88 is larger in diameter than the bore of the cylinder 58, the degree of movement of the piston 98 will be less than the movement of the piston 68. Thus, it will be apparent that by employing the teachings of my invention the presented itself. In such conventional machines it requires very accurate adjustment between each actuator to enable the starting of cutting tools simultaneously. In my above mentioned co-pending applications I have disclosed a needle .86 is operable directly. in response to the valve arrangement for controlling the load between the actuators, and it will be observed that by providing .the. circuit shown in the present application I do not depend on this needle valve arrangement for controlling both of the actuators 56 and 86 during the rapid approach movement. This is due to the fact that the actuator operation of the actuator 56.

As just described, the shifting of the valves I68 and I62 to the left causes the simultaneous rapid traverse of the tools 54 and 82 toward the work piece. The hydraulic clutch actuating mechanism 238 which 'is connected-with the pipes 234 and 248 is also actuated during this interval. The piston 258 thereof is urged to the left, Figure16, thereby connecting the main rear, drive shaft 42 with the work spindle 36. The actuation of the hydraulic mechanism 238 may be timed so that the work spindle 36 begins to ro-. tate and thereby actuates the plunger pumps, 84 and 84a just as thefront and rear tool carriag'es reach the limit of their rapid traverse movement toward the'work piece. At this instant the valve members I68 and I62 are returned to the neutral position shown in Figure 16, and the rotary valve 262 is shifted so as to establish communication between the pipes 268 and 264. It will then be apparent that the plunger pumps 94 and 94a deliver fluid at high pressure to the actuators 68 and 86. Under these is included within a closed circuit which includes.

the. pipe 258, the actuator 68, the pipe 268, and

' thepipe 264.

When the tool carriages reach the limit of their advancing feeding movement, the valve members I 68 and I62 are moved to the rapid traverse reverse position shown in Figure 18.

When the valve members are shifted to this position the hydraulic clutch actuating device 238 is automatically operated so as to disconnect the work spindle 36 from the drive shaft 42, thereby interrupting the actuation of theplungerpumps. Fluid from the low pressure gear pump I 58 is then. directed from the .pipe I52- through the valve port I 54 and into the passage I82. The lateral'passage 226 of 'thevalve member I62-directs a portion of this fluid through the valve port 2I6, and thence outwardly through a pipe line 218 which is connected to the left end of the cylinder 18 through the pipe 268, Figure 16. This causes rapid reverse movement of the piston 12, and fluid from the advancing side of the piston is returned to the valve mechanism I through a section of the pipe line 258, the pipe 268, and the pipe 228, said latter pipe connect- 2 ing with the valve port 2I4. At this instant the valve port 2l4 communicates with the low pressure chamber 2840f the valve mechanism, Figure 18. At the same instant the remaining portion of the fluid from the passage I92 is conducted by a lateral port or passage 212 to the valve port 2I2 which connects with the pipe 242. Low pressure fluid is thus introduced within the rear carriage cylinder 88 so as to impart rapid reverse movement to the piston 98. Fluid from the advancing side of the piston 88 passes through the pipe 248, the actuator 238, and thence through a pipe-214 which connects with ,the valve port 2I8. This valve port- 2I8 like the valve port 2I4 is connected with its com panion low pressure chamber 288.

Attention is directed to the action which takes place at the instant the control valve is shifted to its rapid reverse position. At this time both the rear and front tools are operatively engaging the work piece. Dueto the fact that the front carriage iscmounted'upon the oscillatory bar 48, the weight of the carriage will cooperate to reduce the power necessary to swing the tool 54 out of engagement with the work piece the instant that the control valve is thrown into reverse. In other words, the mechanical arrangement of the front carriage is such as to set up less resistance to reverse fluid action thanthe rear carriage. The rear tool, due to the mechanical had placed on the rear tool slide as a result of the connection which it makes with the automatic control slide, later to be described, and due to the fact that it is horizontally slidable will remain in contact with the work piece'long enough to complete its cut and will not return until the rotation of the work spindle has been -'completely arrested. It will be noted that the Automatic control mechanism I shall-now proceed to describe the means for automatically controlling the actuation of the valve members I68 and I62, as well as the rotary valve member 262. This mechanism includes a slide 216, Figures! to 4 inclusive, which is shiftable along the upper surface of the machine base 38 at the front side of the machine. A rack 218 secured to the underside of the slide 216 is driven from a pinion 288 mounted upon' a shaft 282. This shaft carries a bevel gear 284 at its opposite extremity which meshes with a companion gear 288 on a shaft 288. 'Rotation is imparted to this shaft 288 through the agency of a gear 280 which meshes with a rack bar 292 secured to the underside of the rear carriage slide 18, Figure 3. Thus, 5 when the rear tool carriage is reciprocated toward and away from the work piece, movement is imparted to the slide 216. This slide carries a plurality of dogs 294, 296, 208, 300, and 302. In the drawings the slide 216 is disclosed in the pc- 110 sition which it occupies when the valve members I60 and I62 are in neutral position. The shifting of the valve members I60 and I62 to the left is occasioned by moving the control handle I58 to the right, Figures-1 and 2. This imparts a clock- 15 wise movement to the shaft I18, Figure 4, thereby causing the finger I86 to be swung downwardly. The shifting of the valve members to this rapid approach position causes the forward movement of the rear tool slide 18, as above set forth, and the actuation of this slide causes the slide 216 to be urged to the right, Figures 2 and 4. The dog 288 is so positioned on the slide that when it reaches the finger I86, the lathe tools will have been moved to their work engaging ppsition in 25 readiness to perform a cutting operation upon the work piece. The engagement of the dog 298 with the finger I86 causes the valve members I60 and I62 to be shifted to the neutral position shown in Figure 16. Simultaneously with the actuation 30 of the valve members I60 and I62, or at any other desired interval, the dog 302 is carried into engagement with a finger 304 which is carried upon a shaft 306 extending inwardly from and secured to the rotary valve 262, Figures 4 and 5. This 35 causes the valve 262 to be shifted from the position shown in Figure 5 in a counter-clockwise direction so as to establish communication between the pipes Y280 and 264 through a valve passage 262a. The shifting of the valve 262 ren- 84a, functionally operative so as to efl'ect the feeding movement of the piston 12 to the left, Figure 16. Thus it will be apparent that the dog 802 may be adjustably located upon the slide 216 so as to cause the actuation of the valve 262 at any desired interval of the cycle of operation.

The longitudinal feeding movement of the tool 54, as well as the transverse feeding of the tool 82, continues until the dog 294 carried at the ad- 50 vancing extremity of the slide 216 is moved into finger or lever 308 of the balancing mechanism I 12. The inner extremity of the finger 308 is plvotaily connected to a shank 3I0, which is provided with a head 3I2 at its inner extremity. 55 This head an is provided with longitudinal passageways 3, and when said head occupies the position shown in Figure 8, it serves to close communication between a valve chamber 3I6 and an annular port 3I8. This annular port 3l8 has an unrestricted connection with the reservoir I46 through a passageway320, Figure 7, and a pipe 322, Figures 7 and 16. The engagement of the dog 294 with the finger 308 causes the head 3I2 to be shifted to the position shown in Figure l1, thereby uncovering the annular port 3 I 8 and thus connecting the chamber 3I6, as wall as a corresponding valvechamber 3I6a, with the reservoir I46. This causes an unbalancing of the fluid pressures upon the valve members I60 and I62 due to the fact thatthe fluid from the valve chambers 3I6 and 3I6a is now free to flow back to the reservoir I46. The pressure at the opposite extremities of the valve members causes the Same to be automatically urged to the right, to the position shown in Figure 18. During this tiers theclosed circuit, which includes the pump nism I56.

engagement with the free extremity of a pivoted movement to the right the head 3I2 is engaged by the valve member I60, thereby causing said head'to again close communication between the chamber 3| 6 and the reservoir.

The sudden automatic reversal of the valve members causes fluid to be urged in a reverse direction to the actuators 68 and 86 as above de- 216 to the left, the dog 300 is also moved into engagement with a finger 324 of the valve mechanism 262, thereby automatically shifting said valveto the position shown in Figure 5. In this position communication is interrupted between the pipes 260 and 264, Figure 16, thereby rendering the closed circuit, including the plunger pump 94a, functionally inoperative until a se'cond cycle of operation takes place, at which time the dog 302 causesthe shifting of the valve 262 as above described. In order to more positively assure the proper positioning of the valve member 262, I provide a spring pressed plunger 262b, Figure 5, which is designed to co-operate with companion notches formed in the valve member 262.

Modified valve Referring to Figures 19. to 24 inclusive, it will be seen that I have disclosed a modified valve construction, which is indicated generally by the numeral I56a. This mechanism I56a includes a valve. casing 326, which slidably houses a single valve member 328. When this valve member 328 occupies the neutral position shown in Figures 20 and 21,-fluid from the low pressure pipeline I52 passes through 'an annular valve port 330 and thence through radial ports 332, which communicate at their inner extremity with a central valve passage 334. The left end of this valve passage 334 communicates with a valve chamber 336, which communicates with the reservoir I46 through the pipe 206 in the manner previously described in connection with the valve mecha- Thus,'fluid circulates through the valve mechanism I58a when the valve member 328 occupies the position shown. However, when the valve member is shifted to the left (rapid approach position) in the manner described in connection with the valve mechanism I 56, communication is interrupted between the radial ports 332 and the annular port 330. In this position the annular port 330 communicates with a lateral valve port 338, Figure 21, which communicates with a port 2I4a which corresponds to the port 2I4 of the valve I56. This port 2 I40. may be connected with the actuator 56 by the pipe 228. It

will be noted that in this shifted position of the I ically shifted to its rapid reverse position,'

said valve serves to permit the discharge of low pressure fluid through the ports 2I2a. and 2I6a and the return of fluid bers will not affect the other valve member.

throughthe ports 210a and 2H0. Thus, the single valve mechanism l56a corresponds in functional characteristics to the double valve mechanism I56 in that the rapid approach position of said mechanisms causes low pressure fluid from a single source of supply to be directed through a single valve port to a fluid actuator, which actuator in turn controls the functioning of a second actuator. Also, when said mechanisms occupy their rapid reverse position, fluid from said single source of supply is received through a pinrality of ports and directed to a plurality of actuators for the purpose of rapidly shifting said actuators. One of the advantages resulting from the use of the double type valve mechanism I56 resides in the fact that any variation in pressure of the circuit controlled by one of the valve mem It should be noted that the valve mechanism I 56a. is connected with two independent. feeding circuits, while in the double type mechanism I56, the valve member Hill is connected with one of the circuits, and the valve member I62 is independently connected with another circuit.

Check valve Particular attention is directed to the structure of thecheck valve 232, Figures 15 and 16.

- v by means of a key 3%, and longitudinally slidable within the sleeve 342 is a plunger 366. This plunger is urged downwardly within the casing 340 through the action of a coil spring 348 which is interposed between the plunger-and a removable cap or plug 360. A central passageway 352 in the plunger receives fluid from the pipe 233,

and this fluid is directed into radial ports 355. If the fluid from the pipe 230 is of suflicient pressure to overcome the action of the spring 348, the plunger 366 will be urged upwardly, and when radial ports 35% thereof are carried into communication with an annular passage 358, fluid from said annular passage 358 will flow into the.---

pipe 23%. This check valveis of improved practical construction and is particularly adaptable for use in connection with the fluid circuit de'-- scribed above. The check valve differs from the common forms of check valve in that a certain.

movement of the plunger thereof must take place before fluid will be directed from the pipe 230, to the pipe 23$. It will also be observed that my improved check valve is completely sealed against leakage.

Summary riages are accurately controlled. In fact, the

starting of the cutting action of a plurality of tools can be controlled with extreme accuracy, and these results are obtained without the necessity of employing auxiliary mechanisms. Furthermore, it is only necessary to employ a single source of fluid supply. It will be apparent that my invention provides a hydraulic actuator system, wherein fluid from a single source of sup ply is directed through a single valve to a single actuator, which actuator causes the movement of second actuator is connected with a control mechanism which timingly regulates the starting and stopping, as well as the speed of operation of both of said actuators. The type of control valve which I have described, presents a marked improvement over types which have been employed on both sides thereof, ,so that equal volumes of fluid will be taken into and discharged from opposite sides of the pistons. Obviously this specific piston and piston rod construction is not necessary in instances where suitable vents or bleed passages are employed, such as those disclosed in one of my above mentioned co-pending applications. However, by using the type of construction shown in Fig. 16, I present a closed circuit arrangement whereby the same volume of fluid discharged by the high pressure pump to one s de of the actuator piston, is received by said pump from the opposite side of said piston. In other words, the volume of fluid discharged from the advancing side of the actuator piston is just sufllcient to charge the plunger pump. In view of the fact that I employ the type of plunger pump shown in detail in Figures 12 and 13, it is possible to eliminate the use of relief valves across the closed circuits. If an actuator piston; as for example, the piston is suddenly interrupted in its movement, the plunger pump 94 is rendered functionally inoperative until the obstacle which causes the interruption of the p ston movement, is removed. In other words. if the advancing end of the piston 90 is carried into contact with either end of the pylinder 88 and the spindle 35 continues to rotate. the sudden engagement of the pistonwill automatically render the pump 94 functionally inoperative. That is to say. the rotary mechanism w thin the pump will actuate without eflecting reciprocation of the pump pistons.

It should also be noted in connection with mv improved type of check valve, that it differs from conventional construction. in that, when pressure on the opposite sides of my valve is neutralized, the plunger of the valve will experience no movement, due to the fact that the spring is urging said plunger against the valve seating.

In conventional types of check valves, when the pressure on the opposite sides thereof, is equalized, said valves will not prevent the flow of fluid therethrough. However, in my invention, the flow of fluid from one side of the valve to the other, is positively prevented when the fluid pressure on the opposite sides thereof, is

neutralized.

By having the rear carriage It coupled with a second actuator. It will also be seen that the A the dog carrying slide 216 through the agency of the rack 292,-gear 280, shafts 288, 282, 'etc., said rear carriage is under a greater load during reversal than the front carriage 46. In other words, the front carriage 46 merely reverses along the bar 8 with very little frictional resistance to overcome whereas the rear carriage not only experiences the-friction set up by the engagement of the slide or carriage 18 on the guide frame 80, but all the resistance or load which is established by the mechanism which connects the slide 216 with the rear carriage. With such a construction, it will be apparent that under fluid pressure the front carriage will reach its starting position before the rear carriage. In this way I am able toaccurately control the functioning of the control valve by the carriage which is normally under the greatest load during reversal, a condition which is most advantageous in using hydraulic circuits of the type described and claimed herein. Attention is'also directed to the fact that in my machine the reservoir I46 .is always positioned above the hydraulic actuators so as to preclude the entrance of air within the system.

While I, have disclosed my invention as applied to an automatic lathe construction, it should be understood that said invention is by no means limited to such devices, but is capable of being used in any instance where it is desirable to accurately control the shifting of a'plurality of actuators. Therefore my invention should be limited only by the scope of the appended claims.

- trol the operation of said second actuator and thereby effect simultaneous action of said actuators irrespective of the resistance experienced Having, thus described my invention, what I claim asnew and desire to secure by Letters Patent is:

1. In a hydraulic actuator system, a plurality of fluid operated actuators connectable with machine parts and the like, means for supplying fluid under pressure to one of said actuators for imparting movement thereto, means connecting said last mentioned actuator with a second actuator, whereby said first actuator serves to conby said actuators, and control mechanism for timingly governing the direction andextent of movement of said actuators with respect to each other. Y

2. In a hydraulic actuator system, a plurality of fluid operated actuators, each of said actuators including a cylinder and a piston reciprocable therein, means for supplying fluid under pressure to one of said actuators for effecting the shifting thereof, a duct connecting said last mentioned actuator with a second actuator,

whereby fluid may be forced from said first actuator to eifect' the shifting of said second actuator, and control means for receiving fluid from said fluid supplying means and directing said fluid to at least one of said actuators in accordance with the desired direction of movement with respect to each other.

3. In combination with a plurality of shiftabie machine elements, a fluid operated actuator for each of said elements, means for supplying fluid under pressure to one of said actuators to effect the movement of the machine element associated therewith, a duct for directing fluid from said last mentioned actuator to a second actuator, whereby said flrst actuator will control the actuation of said second actuator and thereby eifect simultaneous action of said actuators irrespective of the resistance experienced by said 4. In a hydraulic actuator system, a plurality of fluid operated actuators, fluid propelling means for supplying fluid under pressure to one of said actuators, means for conducting fluid from said last mentioned actuator to a second actuator, whereby the movement of the first actuator will effect the actuation of the second actuator, thereby causing the speed and starting of said second actuator to be accurately governed by fluid displaced from the advancing side of the first actuator, means for controlling the effective connection .of the fluid propelling means with said first mentioned actuator, and means operatively coupling said control means with one of said actuators whereby said control means is governed in response to the actuation of one .of said actuators.

5. In a hydraulic actuator system, a plurality of fluid operated actuators, fluid propelling means for supplying fluid under pressure to one of ,said actuators, means for conducting fluid from said last mentioned actuator to a second actuator, whereby the movement of the first actuator will effect the actuation of the second actuator, a shiftabie valve mechanism for controlling the connection of the fluid propelling means with said first actuator, and means for operatively connecting said valve mechanism with one of said actuators whereby said valve mechanism is shiftable in response to the actuation of one of said actuators.

6. In combination, with a plurality of shiftabie tool carrying devices, a fluid operated actuator associated with each of said tool carrying devices, means for delivering fluid under pressure to the actuator associated with one of said tool carrying devices, a duct connecting said last.

mentioned actuator with the actuator of a second tool carrying device, whereby the speed of travel of said second tool carrying device is controlled in accordance with the displacement of fluid from the advancing side of the actuator associated with said first tool carrying device to thereby accurately govern the degree of movement of said second actuator, and fluid control means associated with one of "said actuators whereby to initiate a change in the rate and to receive fluid from a second of said actuators, said valve being shiftabie in timed relation with the movement of one of said actuators and a duct connecting said first actuator with said second actuator, whereby said first actuator is adapted to hydraulically control said second actuator.

8. In a hydraulic system of control, a plurality of fluid operated actuators, means for supplying fluid under pressure, a valve mechanism connected with said fluid supplying means, said valve mechanism having a plurality of ports and shiftabie to at least two positions in timed relation with the movement of one .of said actuators ducts connecting said ,valve with said actuators, said valve in one shifted position be-' means to one actuator and to receive fluid from another actuator, and connecting means for' rendering said last mentioned actuator operable in response to the actuation of said first mentionedv actuator. n 1

,9. In a hydraulic system of control, a plurality of fluid operated actuators, means for supplying fluid under pressure, a valve mechanism connected with said fluid supplying means, said valve being shiftable to at least three positionsand having a plurality of outlet and inlet ports, ducts connecting said valve with said actuators, said valve in one position, interrupting communication between the supplying means andsaid actuators,

and in a second'shiftable position adapted to supply fluid to one of said actuators-and receive fluid from another of said actuators, and a duct connecting said first actuator and said second actuator, wherebymovement of said second actuator is occasioned in response to movement of said first actuator, said valve .in a third shifted position being adapted to deliver and receive fluid from a plurality of said actuators.

10. In combination with a hydraulic actuator system, including a plurality of fluid operated actuators, means for supplying fluid under pressure, and a reservoir, a valve mechanism including a valve member shiftable to at least two positions, a port in said valve mechanism which is adapted, when the valve member is shifted to one position, to direct fluid under pressure to one of said actuators, and a second port for contemporaneously receiving fluid from another of said actuators and, for directing said fluid to said reservoir, said valve being adapted in another shifted position to direct fluid under pressure to a plurality of said actuators and to receive fluid from said actuators.

11.-In combination with a hydraulic actuator system, including a plurality of fluid operated actuators, a pumping means, and a fluid reservoir, a valve mechanism having a valve member shiftable to various positions and having a plurality of inlet and outlet ports connectable with said actuators, said-valve in one shifted position being adapted to receive fluid from saidpump and dispatch said fluid to the reservoir, and in a second position to. dispatch fluid under pressure to'a single actuator and receive fluidfrom another single actuator, and in a third position to dispatch fluid to a plurality of actuators and receive fluid froma plurality of actuators.

12. In combination with a hydraulic actuator system, including a pluralityof fluid operated a actuators, a, pump for supplying fluid under pres-- sure, and a reservoir, a valve mechanism includ- (ing a-plurality of -valve.members shiftable with- 1 in a casing, sa id mechanism being hydraulically connectable with the pump and said actuators,

one of said valve members being adapted in one shifted position-to direct fluid under pressure to a single actuator, and the other valve member being adapted the same instant, to receive fluid from another actuator, said valve members in a second shifted position being adapted to dispatch fluid under' pressure to a plurality of 'said actuators and'to receive fluid from a plurality of said actuators.

13. In combination with a plurality of shiftable tool carrying devices. a fluid operated actuator associated with each of said tool carrying devices, a pump for supplying fluid under pressure, a valve for controlling thedelivery of'said fluid under pressure to a first of said actuators,

sponse to the actuation of said first mentioned actuator, and means operable in response to the actuation of said second actuator for controlling the actuation of said valve.

14. In combination with a plurality of shift-' able tool carrying devices, a fluid operated actuator associated with each (if said tool carrying devices, a pump for supplying fluid under pressure, a valve for controlling the delivery of said fluid under pressure to one of said actuators,

fluid conducting means for effecting the starting and speed of a second of said actuators in response to the actuation of said first mentioned actuator, and a member shiftable in response to the actuation of one of said actuators for controlling the actuation of said valve.

15. In a hydraulic actuator system, a plurality of fluid operated actuators, a machine element connected to each of said actuators and shifted thereby, pump means for supplying fluid under pressure, a valve for directing fluid under pressure to one of said actuators, a duct connecting said last mentioned actuator with a second actuator, whereby the speed of said second actuator is controlled by the fluid displaced from said first actuator, rotary work carrying means, driving means therefor, and means operable in response to one of said actuators for controlling the connection between the work carrying means and said driving means.

16. In a hydraulic actuator system, a plurality of fluid operated actuators, a machine element driven by each actuator, a single pumping mechanism for supplying fluid under pressure, a unitary valve mechanism for directing fluid under pressure to one of said actuators, means connecting said actuator with a second actuator, whereby to control the starting and speed of said second actuator, and means operated in timed relation with one of said actuators for controlling the actuationrof said unitary valve mechanism.

, 17. In combination with a plurality of shiftable tool carriages, a fluid operated actuator connected with each tool carriage, a single source of being connected with and operated by said last mentioned actuator, and means operated by one of said actuators for controlling the delivery of fluid from said single source of supply to another actuator.

18. In a materiaLworking apparatus of the class described, a plurality of shiftable machine elements, a fluid operated actuator connected with each element, a constantly drivenlarge displacement pumping mechanism for supplying fluid under pressure, a valve mechanism for controlling the-delivery of fluid from said constantly driven pumping mechanism to a first of said actuators, a duct connecting said last mentioned actuator witha second actuator, whereby the second actuator is driven by said first actuator, and a high pressure fluid propelling means connectable with one of said actuators for propelling said actuators control the operation of said second actuator and travels simultaneously with said second actuator, means connecting said fluid supplying means with another of said actuators, and control mechanism for timingly governing the direction and extent of movement of said actuators.

20. In combination with a plurality of shiftable machine elements, a fluid operated actuator for each element including a piston within a cylinder, means for supplying fluid under pressure to one side of the piston in one of said actuators to effect the movement thereof in a given direction, a duct for directing fluid from the discharge side of said piston to the cylinder of a second actuator, whereby the movement of said second actuator will be controlled in response to the movement experienced by said first mentioned actuator, fluid conducting means connecting said fluid supplying means with another of said fluid operated actuator, and control mechanism for timingly governing the direction and extent of movement of said actuators.

21. In a hydraulic actuator system, large delivery pumping means for supplying fluid under low pressure, a fluid operated actuator, a valve mechanism for controlling the effective connection between said pumping mechanism and said actuator, a second fluid operated actuator, a duct connecting said first actuator with said second actuator, whereby the movement of said second actuator is controlled in response to the movement of the first actuator, a third actuator connectable with said source of low pressure fluid supply, a high pressure pumping mechanism connected with said second fluid operated actuator and a high pressure pumping mechanism connected with said third fluid operated actuator, the low pressure fluid serving to impart rapid traverse to said actuators, and the high pressure fluid serving to' impart feeding movement to said actuators.

22. In material working apparatus of the class described, a plurality of fluid operated actuators, machine elements connected with said actuators and driven thereby, a single source of low pressure large displacement fluid supply, a valve mechanism for controlling the delivery of fluid from said source of supply to one of said actuators, means connecting said actuator with a second actuator, whereby fluid from the first actuator may be forced toward the second actuator for shifting same, a high pressure fluid displacing means connected with said second actuator, driving means for said high pressure fluid displacing means, and means for controlling the connection between said driving means and said high pressure displacing means, said controlling means operating to disconnect the driving means during the displacement of the low pressure fluid to said actuators.

. 23. In material working apparatus of the class described, a machine frame, rotary supporting means, an oscillatory and reciprocable tool support, a second reciprocable tool support, a fluid operated actuator connected with each tool support, means for supplying fluid under pressure to one of said actuators, means connecting said last mentioned actuator with the second actuator, whereby the movement of the second actuator is controlled by said first actuator, and means operable by the tool support associated with one of said actuators for controlling the connection between the source of fluid supply and said first described, a tool supporting means, a bar providing an oscillatory support for said tool supporting means and adapted to reciprocate said tool supside of said cylinder, a pumping mechanism having the intake side connected with the opposite end of said conduit, and a second conduit extending from the discharge side of said pumping mechanism to the other side of said cylinder, the fluid discharged by one side of the piston being equal in volume to the fluid received on the opposite side of said piston and being sufficient to charge said pumping mechanism.

26. In a hydraulic actuator system, a fluid .operated actuator including a piston within a cylinder,

a conduit having one end connected with one side of said cylinder, a variable displacement pumping mechanism having the intake side connected with the opposite end of said conduit, and a second conduit extending from the discharge side of said variable displacement pumping mechanism to the other side of said cylinder, the fluid discharged by one side of the piston being equal in volume to the fluid received on the opposite side of said piston and, being suflicient to charge said variable displacement pumping mechanism.

. 27. In a hydraulic actuator system, a fluid operated actuator including a cylinder, a piston therein, said piston having a piston rod section of equal size extending on opposite sides thereof, whereby fluid taken into one side of the cylinder will be equal in volume to the fluid discharged from the side of the actuator being sufiicient to charge said plunger pump.

28. In a material working apparatus of the class described, a shiftable machine element, a fluid operated actuator for shifting said element, said actuator including a piston within a cylinder, the volume of fluid adapted to be taken into one side of said cylinder being equal to the amount capable of being discharged at the opposite side of said cylinder, a duct connected at one end to one side of said cylinder, a variable displacement pump having its intake side connected to the opposite end of said duct, and a second duct extending from the discharge side of said pump to the other side of said cylinder, whereby fluid from the discharge side of said actuator serves as the sole charging fluid for said displacement pump.

29. In a hydraulic actuator system, a fluid operated actuator including a cylinder and a piston within said cylinder, a variable displacement pump, a closed duct connecting one side of said cylinder with the intake side of said pump, a closed duct "connecting the discharge side of said pump with the other side of said cylinder, wherevariable 7 by to present a closed fluid circuit, and a second fluid operated actuator connectable in series with the first mentioned actuator.

30. In a hydraulic actuator system, a plurality of fluid operated actuators, each of said actuators including a cylinder and a piston therein, means for supplying fluid under pressure to one of said actuators for effecting the shifting thereof, a duct connecting said last mentioned actuator with a second actuator, whereby fluid may be forced from said first actuator to effect the shifting of said second actuator, and a valve in said duct to prevent the reversal of flowof fluidinto said first mentioned actuator.

31. In combination with a hydraulic circuit including a plurality of hydraulic actuators for propelling machine parts and the like, fluid conducting means connecting a pair of said actuators comprising a check valve including a casing, means at one end of said casing for connection with said circuit, means at the opposite end of said casing for connection with said circuit, and a shiftable member within said casing which is adapted upon being shifted a predetermined .amount to establish communication between the opposite ends of said casing. a)

32. In combination with a hydraulic circuit including a plurality of hydraulic actuators for propelling machine parts, and the like, fluid conducting means connecting a pair of said actuators comprising a check valve including a casing, means at one end of said casing for connection with said circuit, means atv the opposite end of said casing for connection withrsaid circuit, a

shiftable member within said casing which is adapted upon being shifted a predetermined amount to establish communication between the opposite ends of said casing, and resilient means for urging said shiftable member in a givendirection.

33. In combination with a hydraulic circuit including a plurality of hydraulic actuators for propelling machine parts and the like, fluid conducting means connecting a pair of said actuators comprising a check valve mechanism including a casing, a plunger within said casing, cooperative ports adapted to establish communication between opposite ends of the casing when said plunger has been shifted a predetermined amount, and resilient means for urging said plunger in'a given direction.

34. In combination with a hydraulic circuit including a plurality of hydraulic actuators for propelling machine parts and the like, fluid con- }ducting means connecting a pair of said actua- =tors comprising a check valve mechanism includ-, ing a casing having an intake'port at one end thereof and a discharge port at the other end thereof, a plunger reciprocable within said casing, said plunger-having a longitudinal passage and a radial port communicating therewith, and resilient means for urging said plunger toward one extremity of said casing.

35. In a hydraulic system for controlling a plurality of fluid operated actuators, a fluid pump mechanism for propelling one of said actuators ata feeding rate, a second fluid pumping mechanism for propelling another of said actuators at a feeding rate, a third fluid pumping mechanism for propelling said actuators at rapid traverse speed, one of said actuators being controlled directly in response to another of said actuators, avalve mechanism for selectively controlling the delivery of fluid from said pumping mechanism to said actuators, a member mechanism driven by one of said actuators, means on/said member for timingly controlling the actuation of said valve mechanism, a second valve mechanism for independently controlling the fluid in connection with one of said actuators, and means on said member for timingly actuating said second valve mechanism.

36. In a hydraulic system for controlling a plurality of fluid operated actuators, a fluid pump mechanism for propelling one of said actuators at a feeding rate, a second fluid mechanism for propelling another of said actuators at a feedin rate, a third fluid pumping mechanism for propelling said actuators at rapid traverse speed, a valve mechanism for selectively controlling the delivery of fiuid from said pumping mechanism to said actuators, a member mechanism driven by one of said actuators, means on said member for timingly controlling the actuation of said valve mechanism, a rotary valve mechanism for independently controlling the fluid in connection with one of said actuators, and means on said member for timingly actuatingsaid rotary mechanism.

37. In a hydraulic valve mechanism for controlling the operation of a plurality of fluid operated actuators, including a casing, a plurality of shiftable valve members in said casing, arranged in substantial parallelisms, and means for connecting and disconnecting said valve members,

whereby to render the same operable independently and also shiftable as a unit within said casing. I 38. A valve mechanism for controlling the operation of a plurality of fluid operated actuators including a casing, a valve member shiftable to at least two positions in said casing, a port in said valve mechanism adapted when the valve member is shifted to one position, to direct fluid to a selected actuator, and a second port for contemporaneously receiving fluid from another actuator, said valve having a plurality of ports whereby when occupying another shifted position, said valve serves to contemporaneously direct fluid to a plurality of said actuators and to receive fluid from said actuators. 39. A system of hydraulic control including a plurality of hydraulic actuators, a relatively high pressure pumping mechanism, a second lower pressure pumping mechanism for propelling said actuator at a relatively rapid rate, shiftable con trol mechanism adapted in one shifted position to direct fluid from said high pressure pumping mechanism to one of said actuators independently 'of said second mentioned pumping mechanism, and fluid conducting means connecting a pair of said actuators, whereby the movement of one actuator is controlled by the fluid displaced from the other actuator.v

40. A system of hydraulic control including a plurality of hydraulic actuators, a relatively high pressure feeding pump, a low pressure rapid traverse pump, control mechanism for rendering the rapid traverse pump functionally inop erative for propelling purposes with respect to at least'one of said actuators during the functioning of the high pressure pump, and fluid conducting means extending between a pair of said actuators, whereby the movement of one actuator is controlled in accordance with the displacement of fluid from the other.

41. In a hydraulic actuator system for moving machine parts and the like, a plurality'of hydraulic actuators connectable with said machine parts, each of said actuators including a piston within a cylinder, fluid propelling means for imparting feeding movement to at least one of said actuators, a second fluid propelling means for imparting rapid traverse movement to at least one of said actuators, a valve for cutting off said second mentioned propelling means during the operative functioning of the other propelling means, and fluid conducting means extending between a pair of said actuators, whereby the movement of one actuator will control the movement of the .otheractuator in accordance with the displacement of fluid from one actuator to the other.

42. In material working apparatus of the class described, a prime mover, a hydraulic actuator inl5 cluding a piston within a cylinder, fluid propelling mechanism driven in timed relation with said prime mover and adapted to imparta linear speed to the actuator piston which is constantly proportional to the speed of travel of said prime mover, means connecting said fluid propelling mechanism with said hydraulic actuator, a second hydraulic actuator including a piston within a cylinder, and fluid conducting means extending between said actuators, whereby one actuator serves as an impeller for the other actuator,

43. In material working apparatus of the class described, a prime mover, a hydraulic actuator including a piston within a cylinder, fluid propelling mechanism driven in timed relation with said prime mover and adapted to impart a linear speed to the actuator piston which is constantly proportional to the speed of travel of said prime mover, means connecting said fluid propelling mechanism with said hydraulic actuator, means for imparting rapid movement to said actuator, a second hydraulic actuator including a piston within a cylinder, and fluid conducting means extending between said actuators, whereby one actuator serves as an impeller for the other actuator.

44. In material working apparatus of the class described, a frame, a spindle rotatably mounted in said frame, a tool carriage shiftable transversely of the spindle, a fluid actuator for moving said carriage, a variable displacement pump driven from the spindle for propelling said actuator, a second oscillatory carriage for moving a tool toward and away from theaxis of the spindle and for moving said tool longitudinally of said spindle, a fluid actuator for longitudinally shifting said second carriage, a second variable displacement pump driven from said spindle for moving said second actuator, a third fluid operated actuator for shifting said carriage towardthe spindle axis, means for imparting rapid traverse to said actuators, and means for selec-,

tively controlling the operative functioning of the variable displacement pumps and the means for imparting rapid movement to said actuators.

45. In a hydraulic actuator system for controlling the movement of and for actuating machine parts and the like, a plurality of hydraulic actuators, each including a piston within a cylinder, fluid propelling mechanism for delivering fluid under relatively high pressure for feeding purposes, a second fluid propelling mechanism for delivering fluid under lower pressure for rapid traverse purposes, a shiftable valve means including a plurality of valve members shiftable as a unit within a casing for selectively controlling the delivery of fluid from the low pressure,

fluid propelling means for rapid traverse purposes to said actuators, said valve means serving in one shifted position to operatively con- 75 nect the low pressure propelling mechanism with the actuators and in another shifted position to render said propelling mechanism. functionall inoperative for propelling purposes.

46. In a hydraulic actuator systemfor moving machine parts and the like; a plurality of hydraulic actuators each including a piston Within a cylinder, a feed pump, a rapid traverse pump,. a fluid reservoir connected with said rapid traverse pump, and shiftable means including a plurality of valve members shiftable as a unit within a casing for controlling the operative functioning of said pumps with respect to the actuators, said valve members being adapted in one shifted position to direct fluid discharged by said rapid traverse pump to the reservoir independently of the fluid discharged by the feed pump and in another shifted position serving to deliver fluid discharged by the rapid traverse pump for rapid traverse purposes to said actuators.

4'7. In a hydraulic actuator system for moving machine parts and the like, a plurality of.

hydraulic actuators each including a piston within a cylinder; a feed pump, a rapid traverse pump, a control device including a plurality of valve members shiftable within a casing, said valve members adapted to occupy one of at least three positions, namely, a neutral position, a forward position, and a reverse position/means connecting said valve members with said rapid traverse pump, said valve members being adapted in their neutral position to effect the circulation of fluid from said rapid traverse pump independently of the fluid discharged by the feed pump, the forward shifted position of said valve members serving to operatively connect said rapid traverse pump with said actuators and the reverse shifted position of said valve serving to direct fluid in a reverse direction to said actuators, and means for rendering the feed pump. functionally inoperative during the operative functioning of said rapid traverse pump.

48. In a hydraulic ,actuator system for controlling the movement of machine parts and the like, a plurality of hydraulic actuators each including a piston within a cylinder, a pumping mechanism for supplying fluid under pressure, a shiftable control valve for controlling the delivery of fluid from said pumping mechanism to at least one of said actuators, and fluid conducting means extending between said actuators,

whereby fluid may be delivered from one actuator to the other for controlling the movement thereof, said conducting means including a valve which is adapted when the control valve is positioned to direct fluid from said pump to at least one of said actuators to permit the flow of fluid through said connecting means in a given direction and when said valve closes communication between said pump and said actuator to prevent the flow of fluid through said connecting means in a reverse direction.

v placement of fluid to effect the movement of the other carriage to thereby accurately control the said pump to said actuators, and fluid conducting means extending between said hydraulic actuators, whereby the actuator of one carriage serves as an impeller for the actuator of the other carriage.

51. In metal working apparatus, a rotatable work support, a front carriage shiftable toward ,7

and away from and longitudinally of the work piece, a rear carriage shiftable toward and away from the work piece, a hydraulic actuator for shifting the carriage toward the work piece, a second hydraulic actuator for moving said carriage longitudinally of the work piece, a third hydraulic actuator for shifting the rear carriage, a pumping mechanism for supplying fluid under pressure, a valve mechanism for controlling the delivery of fluid from said pump to said actuators, and fluid conducting means extending between two of said hydraulic actuators, whereby the movement of one carriage may be accurately timed with'respect to the movement of the other carriage.

' 52. In metal working apparatus, a rotatable work support, a front carriage shiftable toward and away from and longitudinally of the work piece, a rear carriage shiftable toward and away from the work piece, a hydraulic actuator for shifting the carriage toward the work piece, a second hydraulic actuator for moving said carriage longitudinally of the work piece, a third hydraulic actuator for shifting the rear carriage, a pumping mechanism for supplying fluid under pressure, a valve mechanism for controlling the delivery of fluid from said pump to said actuators, and fluid conducting means extending between the firstand third hydraulic actuators, whereby the movement of the rear carriage toward the work piece may be accurately timed with respect to the movement of the front carriage toward the work piece.

53. In metal working apparatus a rotatable work support, a front carriage shiftable toward and away from the work piece, a rear carriage shiftable toward and away from the work piece, a hydraulic actuator connected with the front carriage, a second hydraulic actuator connected with the rear carriage, a rapid traverse pump, a feed pump, a valve for controlling the connection of the rapid traverse pump with said actuators, and connecting means extending between said actuators, whereby the actuator of one carriage serves as an impeller for the actuator of the other carriage when said valve is positioned to render the rapid traverse pump functionally operative.

54. In metal working apparatus; a rotatable work support, a front carriage shiftable toward and away from the work piece, a rear carriage shiftable toward and away from the work piece,

a hydraulic actuator connected with the front carriage, a second hydraulic actuator connected with'the rear carriage,'a rapid traverse pump, a

feed pump, a valve for controlling the connection of the rapid traverse pump with said actuators, connecting means extending between said actuators, whereby the movement of one carriage will be accurately timed with respect to the other carriage when said-valve is positioned to render the rapid traverse pump functionally operative, and means for preventing a reversal of fluid flow within said connecting means when the feed pump is rendered functionally operative.

55. In material working apparatus, a rotatable work support, a front carriage shiftable toward and away from and longitudinally of 'the work piece, a rear carriage shiftable toward and away from the work piece, a hydraulic actuator for shifting the carriage toward the work piece, a second hydraulic actuator for moving said carriage longitudinally of the work piece, a third hydraulic actuator for shifting the rear carriage, pumping means for imparting feeding movement to the second and third hydraulic actuators, a rapid traverse pump, a valve mechanism for controlling the delivery of fluid from the rapid traverse pump to said actuators, and fluid conducting means extending between the flrst and third actuators, whereby the movement of one of said carriages may be accurately timed with respect to the movement of the other carriage when the valve mechanism is positioned for rendering the rapid traverse pump functionally operative.

56. In material working apparatus, a rotatable work support, a front carriage shiftable toward and away from and longitudinally of the work piece, a rear carriage shiftable toward and away from the work piece, a hydraulic actuator for shifting the carriage toward the work piece, a second hydraulic actuator for moving said carriagelongitudinally of the work piece, a third hydraulic actuator for shifting the rear carriage, a feed pump for the second hydraulic actuator, a second feed pump for the third hydraulic actuator, a rapid traverse pumping mechanism, a valve mechanism for controlling the connection of the rapid traverse pumping mechanism with said actuators, and fluid conducting means extending between two of said hydraulic actuators, whereby the movement of one carriage may be accurately timed with respect to the movement of the other carriage.

57. In material working apparatus of the class described, a rotary spindle, a carriage shiftable transversely of the spindle, a second carriage shiftable transversely of said spindle, a hydraulic actuator connected with each carriage, a closed hydraulic circuit which includes one of said actuators and also includes a feed pump, a rapid traverse pump, means for controlling the operative functioning of said latter pump with respect to at least one of said actuators, and fluid connecting means extending between said actuators, whereby the movement of one carriage may be accurately timed with respect to the movement of the other carriage during the operative functioning of said rapid traverse pump.

58. In material working apparatus of the class described, a rotary spindle, a carriage shiftable transversely of the spindle, a second carriage shiftable transversely of said spindle, a hydraulic actuator connected with each carriage, a closed hydraulic circuit which includes one of said actuators and also includes a feed pump operable in synchronism with said spindle, a rapid traverse pump, means for controlling the operative functioning of said latter pump with respect to at least one of said actuators, and fluid connecting means extending between said actuators, whe e-' by the movement of one carriage may be accurately timed with respect to the movement of the.

other carriage during the operative functioning of said rapid traverse pump.

59; In material working apparatus of the class described, a pluralityof shiftable machine elements, a hydraulic actuator connected with each of said elements, a pump, a valve mechanism for of said elements, a pump, a valve mechanism for controlling the operative connection of the pump with said actuators, said valve mechanism including a plurality of shiftable valve members, and means for reducing fluid pressure in a portion of said valve mechanism, whereby to enable the normal fluid pressure in another portion thereof to effect the sudden shifting of said members.

' 61. In material working apparatus of the class described, a shiftable machine element, a hydraulic actuator connected with each element, a pump, a valve mechanism for controlling the operative connection of the pump with said actuator, said valve mechanism including a cylindrical chamber and a valve member longitudinally shiftable within said chamber, and means shiftable longitudinally of said chamber to effect the unbalancing of fluid pressure therein and thereby cause a sudden shifting of said valve member.

62. In combination with a plurality of shiftable tool carrying devices, a fluid operated actuator associated with each of said tool carrying de vices, a pump for supplying fluid under pressure, a valve for controlling the delivery of said fluid under pressure to one of said actuators, fluid conducting means for effecting the starting and speed of a second of said actuators in response to the actuation of said first mentioned actuator, and means shiftable in response to the actuation of one of said actuators for controlling the actuation of said valve.

63. In a hydraulic actuator system, a plurality of fluid operated actuators, a machine element connected to each of said actuators and shifted thereby, pump means for supplying fluid under pressure, a valve for directing fluid under pressure to one of said actuators, a duct connecting said last mentioned actuator with a second actuator, whereby the speed of said second actuator is controlled by the fluid displaced from said first actuator, rotary carryingmeans, driving means therefor, and means operable in response to one of said actuators for controlling the connection between the carrying means and said driving means.

' 64. In a hydraulic actuator system, a plurality of fluid operated actuators, a machine element driven by each actuator, a single pumping mechanism for supplying fluid under pressure, a unitary valve mechanism for directing fluid under pressure to one of said actuators, means connecting said. actuator'with a second actuator, whereby to control the starting and speed of said second actuator, and means operated in timed relation with one of said actuators for controlling the actuation of said unitary valve mechanism.

65. In combination with aplurality of shiftable tool carriages, a fluid operated actuator connected with each tool carriage, a single source of fluid supply connectable with one of said ac 'tuators, a second of said actuators being connected with and operated by said last mentioned actuator, and means operated by one of said actuators for controlling the delivery of fluid from said single source of supply to the other actuator.

66. In material working apparatus of the class described, a plurality of fluid operated actuators,

machine elements connected with said actuators ator, driving means for said high pressure fluid displacing means, and means for controlling the operative functioning of said fluid displacing means, said controlling .means operating to render the high pressure fluid displacing means functionally inoperative during a portion at least of the operating cycle of said actuators.

67. In material working apparatus of the class described, a machine frame, rotary supporting means, an oscillatoryand reciprocable tool support, a second reciprocable tool support, a fluid operated actuator connected with each tool support, means for supplying fluid under pressure to one of said actuators, means connecting said last mentioned actuator with the second actu ator,'whereby the movement of the second actuator is controlled by said first actuator, and means operable by the tool support associated with one of said actuators for controlling the connection between the source of fluid supply and said first actuator. a

68. In a hydraulic actuator system, a plurality of fluid operated actuators, each of, said actuators including a cylinder and a piston reciprocable therein, means for supplying fluid under pressure to one of said actuators for effecting the shifting thereof, a duct connecting said last mentioned actuator with a second actuator, whereby fluid may be forced from said first actuator to efiect the shifting of said second actuator, and valve means associated with said duct for controlling the direction of fluid flow between said actuators.

69. In a hydraulic system 'for controlling a plurality of fluid operated actuators, a fluid pump mechanism for propelling one of said actuators at a feeding rate, a second fluid pumping mechanism for propelling another of said actuators at a feeding rate, a third fluid pumping mechanism for propelling said actuators at rapid traverse speed, one of said actuators being controlled directly in response to another of said actuators, a valve mechanism for selectively controlling the delivery o-f fluid from said pumping mechanism to said actuators, shiftable mechanism driven by one of said actuators, means on said shiftable mechanism for timingly controlling the actuation of saidvalve mechanism, a second valve mechanism for independently controlling the fluid in connection with one of said actuators, and means on said shiftable mechanism

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