US2178364A

US2178364A - Material working apparatus

Info

Publication number: US2178364A
Application number: US481741A
Authority: US
Inventors: Ernest J Svenson
Original assignee: Individual
Current assignee: Babcock and Wilcox Co
Priority date: 1930-09-13
Filing date: 1930-09-13
Publication date: 1939-10-31
Anticipated expiration: 1956-10-31

Description

Oct. 31, 1939. E J. SVENSON MATERIAL WORKING APPARATUS Filed Sept. 13, 1930 5 Sheets-Sheet 1 g lfzvzniow l /w/esi 15212725072 7% a .2 332;zgzzzgs E. J. SVENSON MATERIAL WORKING APPARATUS Oct. 31, 1939.

Filed Sept. 13, 1930 5 Sheets-Sheet 2 Oct. 31, 1939. E J. SVENSON 2.178.364

MATERIAL WORKING APPARATUS Filed Sept. 13, 1930 5 Sheets-Sheet 3 FLU/6771297 lrmeaifSuerwon Oct. 31, 1939. E J. SVENSON MATERIAL WORKING APPARATUS Filed Sept. 13, 1950 5 Sheets-Sheet 4 lZZU/Q7Zt07 2 0 7 E 8 m V 66 r 3% r 6 8 m n H 6 6 1 1 Q T/J; v i Lj.... j4, a.

Patented Oct. 31, 1939 UNITED STATES PATENT OFFICE 15 Claims.

My invention relates generally to material working apparatus, and more particularly to metal working or cutting devices equipped with hydraulic systems of control.

6 It is one of the primary objects of my present invention to provide a hydraulically controlled unit of compact and durable construction, which is readily adaptable for use in many types of ma- ,chines, that is to say, which may be effectively employed in connection with material working devices, such as drilling, boring, grinding, broachlng, planing and milling machines, as well as lathes, hydraulic presses and the like. In other words, my invention contemplates the provision 15 of an improved hydraulic system of control, which may be readily employed for shifting various types of machine elements.

A further object of my inventionis to provide a hydraulic actuator unit for shifting machine 20 elements as above set forth, which is not only of compact and durable construction, but is of very simple construction, thereby enabling the same to be economically manufactured as compared with relatively expensive actuator devices 25 of the mechanical type which have been employed in practice heretofore.

Another object of my invention is to provide a hydraulic actuator unit as above set forth for reciprocating a machine element, such as a drill- 30 ing or boring tool, which unit will function with equal effectiveness in a horizontal, vertical, or

inclined plane, and which is attachable or de- 1 tachable with a minimum amount of skill and effort.

35 Still another object of my invention is to provide a hydraulically operated actuator unit as above set forth which is extremely accurate in effecting the performance of cutting operations,

. and to this end I propose to provide an improved 40 spindle support and a hydraulic actuator arranged in parallelism therewith.

More specifically, my invention contemplates the provision of a multi-slded spindle support which is adapted to be conveniently secured in a 45 fixed position or to reciprocate within a suitable frame to thereby maintain absolute alinement of the spindle which is rotatable within said multisided support.

Still more specifically, my invention contemplates the provision, in combination with the multi-sided support as above set forth, of a hydraulic actuator which is arranged in substantial (parallelism with said support, and which is adapt- 55 ed to reciprocably actuate the same, said support and actuator being conveniently housed within a unitary frame structure.

In addition to the above mentioned advantageous characteristics, my invention contemplates the provision of an actuator unit, in which a prime mover, a plurality of fluid pumping mechanisms, a fluid actuator, and a tool holding mechanism are all supported upon a unitary frame structure which is readily detachable with respect to a suitable support or base.

My invention also contemplates the provision of an improved hydraulic closed circuit arrangement, which includes a variable displacement, high pressure pump, said pump being continuously driven from a suitable prime mover.

The foregoing and numerous other objects and advantages will be more apparent from the following detailed description when considered in connection with the accompanying drawings,

wherein- Figure 1 is an elevational view of a drilling machine which is representative of one embodiment of my invention; I

Figure 2 is a fragmentary plan view of the control slide and associated parts, said slide being shown in its advanced position as distinguished from the starting position shown in Figure 1;

Figure 3 is a transverse sectional view taken substantially along the line 3-4 of Figure 1;

Figure 4 is a vertical sectional view taken substantially along the line 4-4 of Figure 3;

Figure 5 is an enlarged vertical sectional view of the variable displacement pump;

Figure 6 is a transverse sectional view of the pump taken substantially along the line 6-8 of Figure 5; 1

Figure 7 is a fragmentary horizontal sectional view of the rotary valve mechanism taken substantially along the line l--'I of Figure 5:

Figure 8 is a. vertical end sectional view taken substantially along the line 8-4 of Figure 5;

Figure 9 is a perspective view of the mechanism for eccentrically adjusting the driving ring;

Figure 10 is a semi-diagrammatic layout of the hydraulic circuit for controlling the operation of the actuator, the control valve being shown in its initial neutral position;

Figure 11 is an enlarged sectional view of the control valve mechanism shown in Figure 10;

Figure 12 is a horizontal sectional view of said valve mechanism taken substantially along the line l2|2 of Figure 11;

Figure 13 is a sectional view similar to Figure 12, disclosing the valve in its rapid approach position;

Figure 14 is a similar sectional view, disclosing said valve in its rapid reverse positon; and

Figure 15 is a fragmentary sectional view of the right extremity of the valve mechanism, disclosing the unbalanced mechanism shifted to its unbalancing position.

Referring now to the drawings more in detail, wherein I have designated similar parts by like numerals, it will be seen that for the purpose of illustrating one practical application of my invention, I have disclosed said invention in connection with a drilling unit. This drilling unit includes a main head frame 20 which is adapted to be mounted in any suitable manner upon any suitable base, such as the base or main machine frame 22, Figures 1 and 3. The head frame 28 is secured to the base by means of bolts 24, and secured to the underside of the frame 20 by means of bolts 26 is a prime mover or electric motor 28. One end of the frame 28 provides a support for driving and pumping mechanism, later to be described, while the portion of the frame immediately above the motor 28 supports a frame or housing designated generally by the numeral Ill.

The upper portion of this frame or housing 30 provides, a cylinder section 82, while the lower portion of the housing is designed to receive a multi-sided or square spindle supporting member or quill 34. Attention is directed to the fact that the upper or cylinder section 82 of the housing 88 is separated on one side from the lower section of the housing by a slot 38 which extends throughout the length of said housing. Suitable screws 88, Figure 3, extend into the upper and lower sections of the housing 38, and by tightening these screws, said sections may be sprung toward each other. When these sections of the housing are forced toward each other by the screws 38, bearing surfaces III and 42 of said sections are brought to bear against adjacent complementary surfaces of the support member 35, and'similar bearing surfaces Illa and 42a engage companion surface portions of said member. By this arrangement I am able to either positively secure the member 34 against reciprocation within the housing 80, or if it is desirable to reciprocate said member, the adjustment of the screws 38 will serve to take up wear along the aforementioned bearing surfaces.

Positioned within a central opening M of the square member 24 is a rotatable work or tool supporting spindle 46, Figures 3 and 4. Rotation is imparted to this spindle 48 by means of a splined drive shaft 48 which operates within a complementary splined sleeve 50. This sleeve 58 fits over and is coupled with the spindle 46, as clearly shown in Figure 4, and the portion of the sleeve extending away from the spindle is rotatable within a bushing 52 which is secured to the member or quill 34 by means of a pin 8. Thus it will be apparent that the bushing 52 provides the bearing for the inner extremity of the spindle l6.

The outer extremity of the spindle is mounted within suitable anti-friction bearings 58. These bearings are of the preloaded type which are adapted to take up end thrust as well as radial load. A flange 58 formed at the outer end of the spindle 4B is positioned adjacent one side of the bearings 58, and a threaded ring Gil mounted upon the spindle is clamped against the opposite side of the bearings 58. A head 62 encircles the bearings 58 and a flange 84 of said head extends over a ring 86 carried by the adjacent end of the quill 2|. A threaded clamping ring 88 mounted within the outer portion of the head 82 cooperates to secure the head 82 in position upon the quill and the spindle. The upper portion of the head' 82 is formed with a split nut 10, which is mounted upon the threaded outer extremity of a piston rod I2, Figure 4. I

This piston rod I2 is connected at its extremity to a piston I4 which is reciprocable within the cylinder 32. Thus it may be stated that the cylinder 32 and the parts contained therein provide a hydraulic actuator for shifting the spindle and the quill in which it is mounted. A suitable packing box It prevents the leakage of fluid from the cylinder 22. By having the outer extremity of the piston rod 12 threaded, the position of the head 82 with respect thereto may be conveniently adjusted. The hydraulic circuit, of which the cylinder 32 forms a part, will be later described in detail.

Rotation is imparted to the splined drive shaft 48 through the agency of the electric motor 28. The shaft 18 of this motor terminates within a lubricant retaining chamber 80, and fluid within this chamber is secured against leakage along the shaft 18 by means of a suitable packing box 82. The extremity of the shaft I8 carries a pinion or gear 84, which meshes with a larger gear 86 mounted upon a shaft 88. These gears serve as speed reducing gears and a gear carried by the shaft 88 and a second gear 92 meshing therewith and supported by the splined shaft 8, effect the delivery of power from the, shaft 88 to the shaft 48. By having the chamber 80 completely sealed against leakage, the entire unit may be positioned at any angle, or, in other words, may be shiftedbetween vertical and horizontal positions without disturbing the operative effectiveness thereof.

A low pressure large displacement pumping mechanism 84 is mounted upon the main frame 20 by means of bolts 88. This pump 94 is of the gear pump type and includes a suitable casing 88 which houses a pair of meshing gears I80. A drive shaft III2 of the gear pump 84 is connected by means of gears I04 and I88, Figure 4,

I to the drive shaft 88. Fluid supplied to this gear pump is retained within a reservoir I08, which is enclosed within the main frame 20, Figure 1. Fluid from this reservoir I88 is directed througha pipe III! to the intake side of the gear pump ill, and fluid discharged from said pump is directed through a pipe II2 to a valve mechanism III. Fluid at low pressure supplied by the pump 94 is employed to effect rapid traverse of the actuator piston 14, as will later be described, while fluid from a high pressure variable displacement pump II8 is employed to effect feeding movement of the piston II.

This pump IIB, Figures 1. and 5 to 9 inclusive includes a stationary support or casing I I8, which supports a plurality of radially disposed reciprocable pistons I20. 'The outer ends of the chambers in which these pistons are reciprocable communicate with inclined radial passageways I22. Reciprocation is imparted to the pistons I20 through the agency of an eccentrically adjustable driving ring I24, which is mounted on an anti-friction bearing I26, Figures 5 and 6.

This bearing I26 is carried -on the cylindrical portion of a rotary driving member I28, Figures 5 and 9. This driving member I28 is formed with a block or section I38 which is slidably dovetailed within a rotary driving sleeve I32. This driving sleeve I32 is rotatable within a suitable bearing I34 carried by an end casing I20, and rotation is imparted to the sleeve I32 by means of a gear I30 which meshes with companion gear teeth provided along the peripheral surface of a flange I320. 01 the sleeve I32.

Lateral adjustment of the driving member I20 with respect to its driving sleeve I32 is e!- fected by means of a cylindrical adjusting member I40. The inner extremity of this member I40 carries an eccentrically positioned projection I42 which is adapted to be received by a companion slot I44 in the section I30 of the driving member I20. Thus, when rotation is imparted to the member I40 by applying a suitable wrench (not shown) to the outer squared end thereof, the driving member I20 will be shiit ed transversely so as to vary the eccentricity of the driving ring I24 with respect to the axis of rotation of the driving sleeve I32. In other words, by rotating the member I40, the stroke of the pistons will be varied. A nut I46 is adapted to secure the adjusting member I40 in any fixed shifted position. The driving member I20 is provided with a tongue I40 which extends into a companion groove I50, Figure 5, provided in one end of a rotary valve member I52.-

This rotary valve I52 is tapered and the large end thereof is positioned adjacent the driving member I20. A tapered bushing or hearing I54 provides a mounting for the tapered valve I52, and-the outer extremity of said valve member is. provided with a threaded extension I52a. A

. clamping ring I50 mounted upon the threaded end I52a serves to clamp an anti-friction thrust bearing I50 in position. The threaded end I520, of the valve member is split so that when a screw I60 is tightened within the valve member I52, the threaded end. I52a will be sprung outwardly so as to lock the clamping ring I50 in position. With this construction it will be apparent that the valve member I52 may be longitudinally adjusted and positively secured in its adjusted position. The clamping ring I56 and the thrust bearing I50 serve to secure the valve member against longitudinal displacement to the left, Figure 5, and the screw I60 provides an additional lock for said clamping ring. A cover plate I02 extends over the outer end or the stationary support or casing IIB, as clearly shown in Figures and '7.

From the foregoing it will be apparent that the driving member I20 rotates in unison with the tapered valve member I52, and that during this rotation reciprocation is experienced by the pistons I20, in the event that the driving ring I24 is eccentrically positioned, as shown in Figure 6. In this connection it might be stated that pivoted fingers I64 are employed to prevent the subjection oi the pistons or plungers I20 to any undue side thrust. Fluid is introduced to the pump IIIi through a pipe Iii, Figure '7, which communicates with an end chamber I00. Fluid from this chamber I00 passes through passages I provided in the screw I60, and thence into a central valve passage I12. This central valve passage communicates with a peripheral port I14 of the valve member, and thus low pressure fluid from the passage I12 is directed to the passageways I22 which successively register with the peripheral port I". During this registration of the passageways I22 with the-port I14, the plungers I20 companion thereto are experiencing their inward or intake stroke. During the outward or compressing stroke of these plungers, fluid is directed out of, said passageways through a peripheral port I10. This port I communicates through a passageway I10 with an annular port I00, and this annular port is continuously in communication with a discharge pipe I02, Figure '7.

The tapered arrangement of the valve member I52 prevents leakage of fluid longitudinally thereof to the right, Figure 5. Should any fluid be present along the periphery of the tapered valve member at the larger end thereof, an annular passage I04 will convey said fluid through a communicating passage I06, which terminates at its inner extremity within the valve passage I12. By employing the screw I60 and the associated clamping ring I58 in the described manner. I am able to positively secure the valve member against displacement toward its larger end in the event that high fluid pressures are developed which would urge the valve in that direction. By employing this construction, said valve member ,may be subjected to high pressure fluid conditions at either extremity without the slightest possibility of binding. Also, said valve may be accurately adjusted to provide the proper fluid film between the peripheral surface thereof and its bearing for lubrlcation purposes. By using a high pressure plunger pump, such as the pump IIi which is equipped with a stationary housing or support and a tapered valve construction as described, I am able to connect said pump within a closed hydraulic circuit which includes the cylinder 32 and its associated parts, about to be described.

The hydraulic circuit employed for shifting the actuator piston 14 is controlled through the manually or automatically operable valve mechanism II4, Figures 1 and 10 to 14 inclusive. This valve mechanism includes a valve member I00 which is longitudinally shiftable within a casing I00. The shifting of the valve member I00 is occasioned in response to the actuation of a depending arm I92, which is pivotally connected at its lower extremity to the left end of the valve and is mounted at its upper extremity on a horizontal shaft I94. The outer forward extremity of this shaft I94 carries an operating handle I06, and the opposite inner extremity of the shaft supports a pair of fingers 200 and I00, which fingers are respectively positioned in the path of movement of

shiftable dogs

202 and 204, Figures 1 and 2. These

dogs

202 and 204 are adjustably mounted upon a shifter rod 200. which extends between suitable brackets 200 and H0.

When the valve member I00 occupies the neutral position shown in Figures 10, l1, and 12, low pressure fluid from the gear pump 04 is directed from the pipe I I2 to an annular port 2 I2 within the casing I90. At this instant the annular port' 2I2 communicates with radial ports 2I4 in the valve member, and these radial ports direct the fluid into a central longitudinal valve passage 2I6, which communicates at its .left extremity with a valve chamber 2I0. This valve chamber 2I0 is connected with the reservoir I00 by means of a pipe 220 and a suitable needle valve 222. Thus fluid from the valve chamber 2I0 is returned through the pipe 220 and the restricted cation with the central valve passage 2I6 and the end valve chamber 228. Tbe longitudinal valve,passage 2IB communicates with this passage 224 through the agency oi radial ports 22s and an annular valve port 28!. It should be noted that when the valve member occupies this neutral position, a valve section 222 closes a valve port-224, which communicates with a pipe 226, while a similar valve section 238 closes a valve port 240, which communicates with a second pipe 242. In other words, no fluid is delivered to either of the pipes 22! and 242 when the control valve In occupies its neutral position. When the valve member its is shifted to the position shown in Figure 13 by manually manipulating the control handle I98, low pressure fluid from the pipe II2 enters the valve port 2I2, as previously described, and at this interval the valve port 2 I2 communicates with the valve port 224 through a lateral valve passage 244. In this shifted position the radial ports 2" are closed, and thus all of the low pressure fluid is directed from the annular port 224 through the pipe 228. This pipe 236 is connected to one extremity of the actuator cylinder 32, as clearly shown in Figui'e l0. The delivery of fluid from the pipe 236 causes the actuator piston I4 "to be rapidly urged to the left, and fluid from the advancing side of said piston is returned throu h the pipe 242, which at this instant communicates with a lateral valve passage 246, Figure 13. This valve passage 248 causes the fluid from the pipe 242 to be returned through the radial ports 22!, the longitudinal valve passage 2. and the pipe 224 to the reservoir IIII. The shifted position of the valve shown in Figure 13 may be called the rapid approach position because in this position fluid is directed into the cylinder 32 so as to affect the rapid forward or approach movement of the work or tool supporting spindle 46.

This rapid forward or approach movement of the actuator piston II will continue until the dog 244 ismoved into engagement with the oscillatory flnger III. Figures 1 and 2. The engagement of the dog 204 with the finger Ill will cause the valve to be automatically shifted to the neutral position shown in Figure 12. In this position. as previously described, the low pressure fluid supply is out ch from the actuator cylinder 22.

At this point it should be understood that the high pressure pump 6 is continuously operating, and when the actuator piston 14 occupies the position shown in Figures 4 and 10, fluid from the high pressure pump will circulate through the pipe I22, a port 248, the chamber 22a of the cylinder 22, a port 2", and the return pipe line I. However, as the piston 14 begins its movement to the left in response to the introduction of low pressure fluid within the cwlinder I2, as above described, the port 242 will be closed by the piston, and fluid from the pipe I82 will be directed through a longitudinal e 252 and thence through a port 254. Therefore, it

will be apparent that, when the valve memberof the valve casing I, and the shank 2" is longitudinally shiftable within the casing 224. The inner end of the shank 2" is enlarged to provide a head 24.. It will be noted that when the head 2 is positioned, as shown in Figures 10 to 14 inclusive, it serves to close an annular 10 port 2", which is connected through a pipe 214 with the rmervoir Ill. However, when the head 2" isshiftedtothelefhl'lgurc l5,inresponse to the engagement of the dog 2 with the pivoiled lever 2Il,,sald head serves to establish com- 15 munication between the valve chamber 220 andthe annular port Ill through a central passage 212 provided within said head. In this manner fluid pressure withinthe chamber 220 is sumciently reduced so as to cause the automatic g shifting of the valve member III to the right in response to. the pressure oi the fluid within the valve chamber III. This sudden shifting of the valve member in response to the unbalancing oi the fluid at opposite extremitles' thereof causes the valve member to be shifted to the position shown in Figure 14 which might be referred to as the rapid reverse postion.

In this position the valve member causes fluid from thelcw pressure pipe 2 to be directed from the annular port III through the lateral valve passage or port 244 to the port 240, which communicates with the pipe 242. Thus low pressure fluid is delivered in a reverse direction to the cylinder chamber 220 so as to effect the rapid reverse movement oi the actuator piston 14. Fluid from the advancing side of the actuator piston II is returned through the pipe 228 which is at this instant in communication with the valve chamber Ill. During this operation it will be apparent that fluid from the plunger pump H0 is also discharged through the pipe 238. until the. actuator piston I4 reaches the position shown in Figures 4 and 10, at which time fluid fromthe lush pressure pump will again circulate through the cylinder chamber 22c, as above described. As the actuator piston 14 reaches the limit of its reverse movement. the dog 202 is moved into ent with the flnger 20'. thereby causing the automatic shifting of the valve member Ill to its neutral position. A second cycleof 1 M1 mayagalnbeeii'ected by simply moving the control handle I" in a clockwise direction, as viewed in Figure 1.

From fire foregoing it will be apparent that fluidfromthcadvancingsideoftbeactuator piston I4 is employed to charge the: plunger pump Landacloscdbydraulic circuitisprethe pipe I, the plunger pump II, and the pipe I22. I provide a bleed passage or vent 214, Figure 12. in the valve member III in order to takecareoianysllght volumetrlcchangeswlthin the high pressure circuit. scribed circuit arrangement is of extremely sim- 'piedesignandprovidesavcryeifectivesystem of hydraulic control for a machine element of anydcsign. Inothcrwordamyinventionisby The above de- 05 nomeanslimitedtoahydraullcsystemofcon-.

trol in combination with a drilling or boring tool, but contemplates the application of this system ofcontroltoanytypcoi'machine, wherein itis desirable to hydraulically shift an element thereof. Attention ism-in directed to'the arrangement of the hydraulic actuator and the spindle support; By having this multi-sided or square spindle support arranged in parallelism with said actuator, the utmost accuracy in longitudinal or transillatory movement of the spindle is obtained. In some instances it may be desirable to secure the multi-sided spindle support 3| in a fixed position, and this may be accomplished by simply tightening the screws 38. Furthermore, when the spindle support 34 is reciprocated, the screws 38 provide a convenient and easily operated means for bringing the adjacent bearing surfaces together to take up wear. The described fluid circuit lends itself particularly for use with machines wherein the starting and stopping of the spindleare unnecessary, and wherein it is necessary to translate the spindle rearwardly in order to withdraw tools for purposes of reloading, or for the purpose of indexing a work holder and the like. The construction of my device is such as to greatly reduce the cost of manufacture due to the fact that I have eliminated conventional mechanical feeding mechanisms and have provided a hydraulic actuator system which may be'standardized for general application.

It should also be noted that all of the parts, such as the motor, fluid pumps, ears, etc., are completely sealed within suitable housings, thereby positively preventing the accumulation of foreign matter on such parts. Furthermore, all of these parts are readilyaccessible. It will be seen that the prime mover or motor is easily attached to the main frame or casting, and also that the two fluid pumps are readily attachable. The speed of the main drive may be conveniently changed without removing any of the parts, and this arrangement represents a decided improvement over conventional devices. The type of plunger pump which I employ is particularly adaptable for machines of the type disclosed because it may be continuously operated. In the event that the member, such as a tool supported by the spindle, is suddenly interrupted in its movement by making a metal to metal contact, the pressure set up in the closed high pressure circuit will automaticallyrender the high pressure pump functionally inoperative until the obstructing medium is removed. In other words, until this obstruction is removed the eccentric driving ring will operate within the pump without effecting reciprocation of the plungers. The hydraulic actuator serves in this particular instance as a valve for controlling the delivery of fluid from the high pressure pump. In other words, the actuator serves as a means for controlling the functioning of the high pressure fluid circuit.

The head 52 which is mounted upon one extremity of the multi-sided spindle support provides a means for supporting various forms of attachments (not shown), such as spindles or other cutting devices. It should also be noted that this head 62 may be disconnected from the piston rod of the actuator, thereby enabling said rod to be attached to other reciprocating parts. In such instances it may be desirable to clamp the multisided support against reciprocation. In other words, my device has a broad range of application in connection with the control of the reciprocation of machine elements.

It will be noted in Fig. 4 that the head 62 is provided with a lateral flange having a surface designed to receive and support various types of tool attachments. In performing some cutting operations it is desirable to employ attachments equipped with a plurality of tool spindles. In such instances these tool spindles are driven from the main spindle 46. Under such circumstances the multi-sided arrangement of the spindle supporting sleeve, 34 and its companion mounting serves eflectively to prevent any lateral displacement or torsional twisting of the sleeve which might otherwise result from the load experienced by the cutting tools during the operative functioning thereof.

The particular arrangement of my tapered valve presents numerous practical advantages. When the valve is stationary, the annular port Hi4 serves as a means for directing fluid for lubrieating purposes to the peripheral surface of the valve, and when the valve is rotating, this port not only serves to facilitate lubrication, but positively prevents fluid from passing beyond the larger end of the valve, and thereby prevents leakage into the chamber immediately adjacent thereto. Furthermore, by having the end thrust take-up mechanism positioned at the smaller end of the valve I am able to subject said valve to high pressure on either side without in the slightest degree aflecting the eilicient functioning thereof. I have subjected valves of this type to severe operating conditions, and after the device was operated over an extended period of time, no appreciable wear could be detected. The valve may be longitudinally adjusted to provide the proper oil film between the surface of the valve and its bearing for various rotative speeds. By reason of the fact that the valve positively precludes any leakage, the displacement of the pump may be varied between zero and maximum without experiencing any pulsative action in the hydraulic system with which it is connected.

Attention is again directed to the fact that my invention enables the provision of a self-con-v tained complete metal removing apparatus, such as a drill unit which may be positioned in any plane or may be shifted from place to place with great ease. Heretofore metal removing devices have been employed which comprise a plurality of devices, such as drill mechanisms distributed along a suitable bed, but these devices do not comprise individual self-contained complete operating units of the type set forth above and shown in the drawing. In these conventional machines it has been the common practice to employa central source of hydraulic fluid supply for a plurality of drilling devices as distinguished from my improved "unit construction, wherein the hydraulic source of power supply for reciprocating a support, such as a drill holder, as well as the power supply, such as an electric motor for imparting rotation to said holder. are all contained within a single portable unit. This unit may be shifted from place to place, positioned at any angle and employed in the same sense as a portable hand drill. Obviously the unit may be relatively large when employed for heavy duty work, or when designed for lighter work it may be relatively small in size. By employing the multisided square quill construction I eliminate the necessity ofusing a conventional key and present a much stronger construction. This multi-sided arrangement positively prevents any twisting of the parts as a result of the operating load to which the cutting tool is subjected. The fact that the high pressure plunger pump is automatically rendered functionally inoperative when the cutting tool meets with an obstruction, renders my described unit particularly applicable for use in instances where a plurality of units, such as drill units are required. In other words, when such units are arranged in multiple, the source of fluid pressure supply may be rendered functionally inoperative in one unit without affecting the source of supply in the other units. This is to be contrasted with conventional multiple type machines, such as multiple drilling machines wherein the breakdown of one drilling device will directly elect the functioning of the other drilling devices, because each device is not a self-contained independently operable unit. Another advantageoiis feature of my invention resides in the fact that my unit may be mounted in any convenient position, and in that position will perform a complete cycle of operation by merely manipulating a control handle in a single direction. It might be stated that my improved self-contained compact portable unit supplies the present demand in the machine tool industry for standardized equipment. In other words, my invention enables the standardization of machining apparatus, and thereby eliminates the necessity of constructing relatively expensive special machines for each particular type of work to be performed.

In connection with the particular type of fluid circuit disclosed in the drawings, attention is directed to the fact that the fluid pressure within the cylinder 32, Figure 10, set up during the circulation of the fluid through the plunger pump 8 is sufficient to maintain the actuator piston I4, and consequently the rotary spindle 46 in their proper starting positions. The circuits which control the hydraulic actuation of the actuator piston may be referred to as primary and secondary circuits, one of said circuits being employed for rapid traverse purposes, and the other for slower or feeding speeds. By placing the prime mover or electric motor 28 beneath the spindle in the manner shown, as distinguished from positioning said motor in substantial axial alinement with the spindle, I am able to reduce the over-all length of the unit and thereby render the same more compact, and keep the motor free from dust accumulation and the like. It should also be noted that in my present construction the spindle is directly coupled through the agency of the gear I88 with the periphery of the driving member I82, and this presents a very practical and simple driving arrangement.

Having thus described my invention, what I claim as new and desire to secure by Letters Patent is:

1. 1n material working apparatus, a multisided sleeve having oppositely disposed bearing surfaces, a rotatable spindle within said sleeve. rotary spindle driving means comprising a shaft extending within said sleeve and slidably connected with said spindle, hydraulic feeding mechanism for said sleeve driven from said shaft, and a mounting for said sleeve having oppositely disposed surfaces companion to the bearing surfaces of said sleeve whereby to secure said sleeve against lateral displacement and torsion, said sleeve being adapted for reciprocation within said mounting to efl'ect the translation of said spindle and serving as the sole lateral support for said spindle whereby to present a self-contained spindle supporting unit.

2. In material working apparatus, a multisided sleeve having oppositely disposed bearing surfaces, a rotatable spindle within said sleeve, means for rotating said spindle, a mounting having oppositely disposed bearing surfaces for receiving and guiding the bearing surfaces of said sleeve to thereby secure said sleeve against lateral displacement and torsion, said sleeve being adapted for reciprocation within said mounting to effect the translation of said spindle, a reciprocable hydraulic actuator including a piston and cylinder construction positioned laterally of said sleeve, hydraulic mechanism includin pumping means and control mechanism for effecting and controlling hydraulic reciprocation of said actuator, the multi-sided sleeve extending in the direction of travel of said actuator and cooperating to maintain the alinement of said actuator during the operative functioning thereof, and means carried by said sleeve as a unit thereof and rigidly connecting said sleeve with said actuator.

3. In material working apparatus, a multisided sleeve having oppositely disposed bearing surfaces, a rotatable spindle within said ,sleeve, means for rotating said spindle, a mounting having oppositely disposed bearing surfaces for receiving and guiding the oppositely disposed bearing surfaces of said sleeve to thereby secure said sleeve against lateral displacement and torsion, said sleeve being adapted for hydraulic reciprocation within said mounting to effect the translation of said spindle, means for securing said sleeve within said mounting, a hydraulic actuator positioned adjacent and laterally of said sleeve, said sleeve extending in the direction of travel of said actuator and cooperating to maintain the alinement of said actuator during the operative functioning thereohhydraulic mechanism includ ing pumping means and control mechanism for effecting and controlling hydraulic reciprocation of said actuator, and means carried by said sleeve as a unit thereof and rigidly connecting said sleeve with said actuator.

4. In material working apparatus, a. multisided sleeve having oppositely disposed bearin surfaces, a rotatable spindle within said sleeve. means for rotating said spindle, a mounting having oppositely disposed bearing surfaces for receiving and guiding the bearing surfaces of said sleeve to thereby secure said sleeve against lateral displacement and torsion, said sleeve being adapted for reciprocation within said mounting to effect the translation of said spindle, a hydraulic actuator including a cylinder and a piston reciprocable therein for hydraulically imparting reciprocable translation, to said spindle, hydraulic mechanism including pumping means and control mechanism for automatically effecting and controlling hydraulic reciprocation of said actuator, said actuator being positioned laterally of and in parallelism with the axis of said spindle, the sleeve cooperating to maintain the alinement of said actuator during its operative functioning, and means carried by said sleeve as a unit thereof and connecting said sleeve with said actuator.

5. In material working apparatus, a multisided sleeve having oppositely disposed bearing surfaces, a rotatable spindle within said sleeve, means for rotating said spindle, a mounting having oppositely disposed bearing surfaces for receiving and guiding said bearing surfaces of said sleeve, said sleeve being adapted for hydraulic reciprocation within said mounting to effect the translation of said spindle, hydraulic mechanism including pumping means and control mechanism for effecting and controlling hydraulic reciprocation of said sleeve and a head on said sleeve having a transverse surface adapted to detachably receive suitabale external attachments,

said bearing surfaces in the sleeve and mounting serving to secure said sleeve and consequently the head carried thereby against lateral displacement and torsion.

6. In material working apparatus, a multisided sleeve having oppositely disposed bearing surfaces, a rotatable spindle within said sleeve, means for rotating said spindle, a mounting having oppositely disposed bearing surfaces for receiving and guiding the bearing surfaces of said sleeve, said sleeve being adapted for reciprocation within said mounting to effect the translation of said spindle, a reciprocable hydraulic actuator including a cylinder and piston construction for imparting translation to said sleeve, hydraulic mechanism including pumping means and control means for effecting and controlling hydraulic reciprocation of said actuator at variable speeds, said sleeve cooperatively arranged for maintaining the alinement of the actuator during the op erative functioning thereof, and an adjustable connection between the sleeve and said actuator, said connection being carried as a unit by said sleeve, said bearing surfaces serving to prevent lateral displacement of said connection and the actuator structure with which it connects.

7. In material working apparatus, a supporting frame, a multi-sided elongated sleeve, a tool driving element rotatably mounted within said sleeve, a hydraulic actuator coupled with said sleeve, hydraulic mechanism including pumping means and control mechanism for effecting and controlling hydraulic reciprocation of said actuator, a split mounting on said supporting frame providing a pair of sections for slidably receiving said sleeve, one of said sections being rigidly supported on said frame to provide a fixed abutment and the other being yieldable with respect thereto, and means for urging said yieldable section toward the sides of said sleeve, whereby to take up wear resulting from reciprocation of the sleeve within the mounting.

8. In material working apparatus, a unitary frame having oppositely disposed bearing surfaces, a hydraulic actuator including a piston and a piston rod reciprocably mounted within said frame, a multi-sided sleeve reciprocably mounted within said unitary frame and having bearing surfaces adapted to be received and guided by the bearing surfaces of said frame, hydraulic mechanism including pumping means and control mechanism for effecting and controlling hydraulic reciprocation of said actuator, said sleeve being spaced from and arranged in parallelism with the axis of said actuator piston, a spindle rotatably mounted within said sleeve, a rigid connection between said sleeve and said actuator, and means for imparting rotation to said spindle.

9. In material working apparatus, a unitary frame having oppositely disposed bearing surfaces, a hydraulic actuator including a piston and a piston rod reciprocably mounted within said frame, a multi-sided sleeve reciprocably mounted within said unitary frame, and having bearing surfaces adapted to be received and guided by the bearing surfaces of said frame, hydraulic mechanism including pumping means and control mechanism for effecting and controlling hydraulic reciprocation of said actuator, said sleeve being spaced from and arranged in substantial parallelism with the axis of said actuator piston, a spindle rotatably mounted within said sleeve, connecting means between the sleeve and actuator, means for driving said spindle, and a splined connection between said driving means and said spindle.

10. In material working apparatus, a multisided sleeve having oppositely disposed bearing surfaces, a rotatable spindle within said sleeve,

means for rotating said spindle, a mounting havingoppositely disposed bearing surfaces for receiving and guiding the bearing surfaces of said sleeve to thereby secure said sleeve against lateral displacement and torsion, said sleeve being adapted for reciprocation within said mounting to effect the translation of said spindle, a reciprocable hydraulic actuator including a piston and cylinder construction for hydraulically imparting variable speed translation to said sleeve, hydraulic mechanism including pumping means and control mechanism for effecting and controlling hydraulic reciprocation of said actuator, said sleeve extending in the direction of travel of said actuator and cooperating to maintain the alinement of said actuator during the operative functioning thereof, and means carried by said sleeve as a unit thereof and rigidly connecting said sleeve with said actuator. I

11. In material working apparatus, a multisided reciprocable sleeve for internally supporting a spindle, a rotatable spindle in said sleeve, means for rotating said spindle, a hydraulic actuator including a piston and cylinder construction for hydraulically imparting reciprocation to said sleeve, hydraulic mechanism including pumping means and control mechanism for effecting and controlling hydraulic reciprocation of said actuator, and a unitary mounting for maintaining the alinement of said hydraulic actuator and said sleeve during the longitudinal translation thereof, said mounting forming a portion at least of the cylinder structure of the actuator whereby to present a compact, rigid unitary construction. a

12. A metal working machine comprising a housing, quill supporting means associated with said housing, a quill coaxial with said supporting means and slidably mounted therein, a spindle journaled in said quill and coaxial therewith, a hydraulic actuator coupled with said quill and extending in the general direction thereof, fluid pressure generating means adapted to hydraulically reciprocate said actuator for imparting reciprocation to said quill, and means for rotating said spindle.

13. In material working apparatus, a reciprocable spindle supporting sleeve, a rotatable spindle within said sleeve, rotary spindle driving means comprising a shaft extending within said sleeve and rotatably and slidably connected with said spindle, hydraulic feed mechanism for said supporting sleeve driven in synchronism with said shaft, a housing for said supporting sleeve having means therein cooperatively arranged to prevent angular shifting of the sleeve during reciprocation thereof, said sleeve being adapted for reciprocation within said housing to effect the translation of said spindle and serving as the sole lateral support for the spindle whereby to present a self-contained spindle supporting unit.

14. In material working apparatus, a reciprocable spindle supporting sleeve, a rotatable spindle within said sleeve, rotary spindle driving means comprising a shaft extending within said sleeve and rotatably and slidably connected with said spindle for driving purposes, hydraulic feed and rapid traverse mechanism for said supporting sleeve driven in synchronism with said shaft, a housing for said supporting sleeve hav- 78 ing means therein cooperatively arranged to prevent angular shifting of the sleeve during the reciprocation thereof. said sleeve being adapted for reciprocation within said housing to eflect the translation of said spindle and serving as the sole lateral support for the spindle whereby to present a self-contained spindle supporting unit.

15. In a metal working machine, a main frame, a reciprocabie spindle supporting sleeve supported by said frame, a rotatable spindle within said sleeve, a housing arrangement for said supporting sleeve having means cooperatively arranged to prevent angular shifting of the sleeve during the reciprocation thereof, rotary spindle driving means comprising a shaft extending within said sleeve and rotatably and slldably connected with said spindle for driving purposes, a second shaft, pick-ofl gears for adjusting the speed between said first and second shafts, hydraulic feedand rapid traverse mechanisms for shifting said supporting sleeve' and driven in synchronism with said shafts, a control member shiftable with said supporting sleeve, control abutment means on said control member for controlling speed of travel and direction of reciprocation of said spindle sleeve, and a control means shiitable in response to action imparted by said abutment means whereby to automatically control speed of travel and reversal of said supporting sleeve in accordance with a preselected cycie of reciprocation.

ERNEST J. SVENSON.

,DISCLAIMER 2,178,364f-Emest J. Samson, Rockford, Il1. MATERIAL WORKING APPARAT s Patent dated. October 31, 1939. Disclaimer filed September 24, I943,

the assignee, Odin Corporation.

Hereby enters this disclaimer to claims 12, 13, and 14.

[Oflicial Gazette November 9, 1943.]

ing means therein cooperatively arranged to prevent angular shifting of the sleeve during the reciprocation thereof. said sleeve being adapted for reciprocation within said housing to eflect the translation of said spindle and serving as the sole lateral support for the spindle whereby to present a self-contained spindle supporting unit.

ERNEST J. SVENSON.

the assignee, Odin Corporation.

Hereby enters this disclaimer to claims 12, 13, and 14.

[Oflicial Gazette November 9, 1943.]