US2372692A - Material working apparatus - Google Patents

Description

April 3, 1945. E. J. SVENSON 2,372,692

MATERIAL WORKING APPARATUS Filed Sept. 9 1929 11 Sheets-Sheet 1 April 3, 1945,. E. J. SVENSON MATERIAL WORKING APPARATUS Filed-Sept. 9, 1929 ll Sheets-Sheet 2 April 3, 1945. E E N 2,372,692

MATERII KL WORKING APPARATUS Filed Sept. 9, 1929 ll Sheets-Sheet 3 E. .1. SV ENSON THRILL WORKING APPARATUS April 3,1945,

Filed Sept. 9; 1929 -ll Sheets-Sheet 4 f A ril 3, 1945. E. J. SVENSON MATERIAL WORKING APPARATUS ll Sheets-Sheet 5 Filed Sept. 9 1929 April '3, 1945. E. J. SVENSON MATERIAL WORKING APPARATUS Filed Sept. 9, 1929 ll Sheets-Sheet 6 QQN . EJ277167 Er/wETJ 5112725071 aim lumimimk GEE wwkmxwk Qwmk wfi 5% QQN mmm April 3, 1945. J SVENSQN 7 2,372,692

MATERIAL WORKING APPARATUS I Filed Sept. '9 1929 I 11 Sheets-Sheet 7 EJ277157 K7 7225771 5711 17205071 April 45. E. J. SVENSON 2,372,692

MATERIAL WORKING APPARATUS Filed Sept. 9, 1929 ll Sheets-Sheet 8 IEiuzfiZBr B N-LEI 5712725071 April 3, 1945. E. J. 'svENsoN 2,372,592

MATERIAL WORKING APPARATUS Filed se i. 9 1929 11 sheets-sheet 9 """HHIIH I m 2522 ZnnesZiISvavwon w Q26 J5; ay

April 3, 1945. E. J. SVENSON 2,372,692

MATERIAL WORKING APPARATUS I Filed Se t. 9 1929 11 Sheets-Sheet 11 w 3w mum LF 2 m QQN -i R NN Patented Apr. 3, 1945 ES "PATEN 1* OFFICE 'MATEBIAL WORKING Ernest J. Svenson, Rockford, 11L, assignon by memo assignments, to Odin Corporation, Cliicago, 111.. a corporation of Illinois Application September 9, 1929, Serial No. 891,180 81 (cl. sz-z) My invention relates generally to material working apparatus and more particularly to automatic lathes and machines of like nature.

One of the problems which confronts manufactures at the present time is that of supplying machines which are capable of producing work at a speed which is commensurate with the demands in industry for more rapid production and for lower costs of manufacture. To meet this situation materialworking machines such as lathes, screw machines and the like have been provided. In many instances these machines have been designed to produce a particular type of work, and to design and build a special machine of this type requires the expenditure of considerable time and money. In many instances after the special machines have been completed, the part or work which was to be produced or machined thereby has been changed in form,, thus rendering this specific machine obsolete and non-productive.

Special machines require trained operators, and obviously in using such devices an unusually large number of different machines must necessarily be employed in a single plant which, of course, requires considerable non-productive supervision. The cost of maintaining such machines is comparatively high due to the time and efiort spent in repairing and replacing specific parts thereof.

It is a primaryobject of my invention to provide a material working machine or apparatus which will avoid the above mentioned and numerous other disadvantages which have heretofore been experienced and to this end I propose to provide a fully automatic machine of simple,

a machine of the instant nature which is so designed that when the same is subjected to overload conditions, the stopping thereof will be efiected without the slightest possibility of breakage of any of the constituent cooperating parts.

Still another object of my present invention is to provide a fully automatic lathe which may said handle serving to cause rotation of the supported work, the operative association of the tools "with the work, the forward feeding of the tools,

the withdrawal of the tools and the automatic return of the tools to their starting position.

In addition; I propose toprovide a material working apparatus in which the speed with which the tools are moved, is automatically and hydraulically controlled in' aunique and expeditiousv manner.

My invention further contemplates the provision 01' a hydraulic control mechanism in which a single automatic valve is employed to control all of the movements of the work supporting spindle and the tool surpports or carriages, said single or unitary valve being also designed for manual as well as automatic manipulation.

The present invention also contemplates the provision of a lathe or machine of like nature having a plurality of cutting tools which are automatically reversible when they have reached the limit of their advancing movement, the reversing movement imparted to the tools being controlled by the tool which is last to complete its advancing or cutting stroke.

To attain these and other objects and advantages and in accordance with the general features of the invention, one embodiment of said invention includes a suitable rotary work supporting spindle having improved bearings for supporting the same in the head-stock. A front tool carriage is provided which is supported by a cylindrical bar, said bar being longitudinally clockwise direction as viewed from the work supporting end thereof and a tail-stock is provided which is equipped with a hydraulically controlled and specially mounted centering element. A suitable unitary oil pump is employed to supply oil pressure for actuating the tool carriages and also for controlling a clutch mechanism on the main drive as well as the tail-stock center. By moving a single control lever which actuates a novel valve arrangement of unitary construction, the tool carriages in one illustrative cycle are rapidly moved into operative position, and at a predetermined stage said tools are moved at a suitable feeding speed across the work surface. When said tools have reached the limit of their movement, a mechanism which is controlled by the tool carriage last to reach its limiting position, operates said valve mechanism to cause a rapid reversal of the carriages to their starting lever and link' mechanism for controlling the,

oscillatory movement of the main oil control valve, said view being tak'en substantially along the line |2-l2 of Figure Figure 13 is an enlarged central sectional view of one extremity of the main valve unit disclosing the advanced position of the valve within its cas- Ill very eiiiicently operable machine having an unusually small number of parts.

Having presented the foregoing general statement relating to the functional characteristics of a machine representing one embodiment of my invention, I will now proceed to describe said machine in connection with the accompanying drawings, wherein:

Figure 1 is a plan view of the machine, the tool carriages being shown in their initial positions, that is, the positions which they occupy prior to the advancement thereof toward the rotatably supported work; a

Figure 2 is a front elevational view of themechine shown in Figure l, the tool carriage in this figure being shown at the limit of its. advanced position, as distinguished from the initial or starting position shown in Figure 1;

Figure 3 is a rear elevational view of the machine, disclosing the rear tool carriage at the limit of its advanced position, corresponding to the advanced position of the front carriage as shown in Figure 2;

Figure 4 is a vertical transverse sectional view taken substantially along the line 4-4 of Figure 2;

Figure 5 is an elevational view of a conventional oil pump mechanism which is detachably mounted at one end of the machine;

Figure 6 is a vertical sectional view taken longitudinally of the machine substantially along the line 6-6 of Figure 4; v

Figure 7 is an enlarged. fragmentary vertical sectional view taken along the line 1-1 of Figure 1, disclosing the arrangement of the single lever control device when the tool supporting carriages main valve structure taken substantially along the line llil of Figure 13; a

Figure 15 is a transverse sectional view taken substantially along the line iii-II of Figure 18;

Figure 16 is a transverse sectional view similar to Figure 14 disclosing the valve after the same has been rotated to its pressure relieving position;

Figure 17 is an enlarged transverse sectional view of the distributor or orifice valve unit which along the line -20 of Figure 19;

have reached the limit of their advancing movek ment and the lever occupies its neutral position; Figure 8 is a plan view of the dog supporting slide and rack and pinion mechanism for operating same;

Figure 9 is an enlarged plan view of the oil control mechanism including the single lever mechanism, the main unitary control valve, and the distributor valve unit, said distributor and main valve units being shown in section for the purpose of more clearly illustrating the functional characteristics of these parts, all of said parts being shown in the position correspofiding'with the neutral position of the control lever shown in Figure 7 when the tool carriages have reached their adanvecd position;

Figure 10 is a vertical transverse sectional view of the oil control mechanisms taken substantially along the line ll--lil ofFigure 9;

Figure 11 is an enlarged vertical sectional view taken-transversely of the rear tool carriage, said section being taken substantially along the line I l-l l of Figure 4; v

Figure 12 is a detailed'elevational view of the Figure 21 is an enlarged fragmentary sectional view of the mechanism for controlling the supply v of oil to the tail-stock piston, said view being taken substantially along the line 2l.2l of Figure l a Figure 22 is a diagrammatic representation of the oil system and valve control mechanisms therefor, the maincontrol valve being shown in its neutral position and the pistons corresponding to each actuated machine unit being shown in their starting position; and I Figures 23 to 26 inclusive disclosed the following positions of the single valve unit: Figure 23 rapid approach or traverse position, Figure 24 feeding position, Figure 25 rapid reverse position, and Figure 26 slow speed reverse position.

In order to clearly present the description oi" the machine disclosed in the foregoing figures, I propose to successively describe various units which constitute the'machine structure.

Head-stock The machine shown in the drawings comprises a head-stock which I have designated generally by the numeral 30 which includes a housing or frame 32 formed at the upper portion of amain frame 34. Thismain frame 34 rests upon a suitable base 35 as shown in Figures 1, 2 and 3. A spindle 38 is rotatably mounted at one extremity within an anti-friction bearing 40 and the opposite work supporting extremity of the spindle is mounted within a tapered bearing 42, Figure'6. The internal surface of this bearing 42 is tapered to receive a companion tapered surface of the spindle 38 and a set screw H is provided to secure said bearing against rotation within the housing 32. The outer extremity of the spindle is flanged to present a face-plate 46. The spindle is pro? vided with an aperture having tapered walls 48 bearings are of such a construction as to allow both radial and thrust load and these bearings Figure 14 is a transverse sectional view of the asvaeea are of the non-adjustable By having the anti-friction. bearing and the bearing 2, the v spindle 38 may be properly aligned between its forward and rear extremities. The spindle I.

carries a gear 52, Figures 6 and 18, which meshes Tail-stock Supported upon the main frame ll is a tailstock which I have designated generally by the numeral 52, Figures 1 to 4 inclusive and Figure 6. This tail-stock 62 comprises a casing or body I and reciprocably mounted within said casing is a spindle or sleeve 66 which carries a centerpiece /68. This center-piece 82 is mounted at both extremities within anti-friction bearings II and 12 which simulate the above mentioned spindle bearings ill. The inner end of the center member t8 supports a bearing block 14 and this hearing block 14 is adapted to be engaged centrally thereof by a ball 16 which is housed within a threaded plug 1.8. The bearings" and 12 serve to retain the center-piece B8 in perfect alignment and the ball 18 provides a very effective means in conjunction with the anti-friction bearings for taking up end thrust which might be occasioned when the center-piece is brought into operativeassociation with the work The threaded end of a piston rod Bil is mounted within the inner extremity ofthe sleeve 68 and the opposite extremity of said piston rod is connected with a piston proper 82 which is reciprocable within a cylinder II. A threaded collar 86 and clamping ring 81 are positioned adjacent the outer end of the sleeve 65 and these parts serve to facilitate the mounting of the center-piece rotatably within the sleeve.

To effectively clamp the sleeve 66 in various positions of longitudinal adjustment, I provide an operating handle 88 which is pivoted at the rear side of the casing 84. As will be seen from Figure 3, the rear side of the casing 84 is split,

cation between ports Ilii and ill. This causes pressure to be applied and thereby eifect the movement of the center-piece to the right. Thus, in addition to unciamping' the sleeve 66 movement of the operating handle causes the centerpiece to be automatically moved out of engagement with the work supported'thereby. nuiar passage llil in the valve 92 serves to establish communication between the ports Hi2 and Ill through a central valve passage illwto permit the egress of oil from the advancing side of the piston 82 when oil is introduced through the ports I and It/As clearly shown in Figure 22, the chamber adjacent the inner end of the valve 12. establishes communication between the ports 1'2 and I to effect the discharge of oil from the advancing end of the piston when the tailstock center-piece B8 is being moved to the right.

In order to further facilitate the convenient against rotation and in propervertical relation by a set screw I". Thus, the longitudinal movement of the center-piece 68 is automatically controlled in response to the movement of the handle 88 and by having the above mentioned ball-bearing mounting, said handle may be moved with a minimum amount of exertion on' the part of the operator.

and the rotation of the handle 88 from the pool-.

92 which is connected to the operating handle or lever 88 by means of a link 94. The valve 02 is reciprocable within a casing 9i and is provided with annular passages 98 and I". The passage 98, when positioned as shown in Figure 21, establishes communication between cylinder ports ill and IM, thereby permitting oil to be introduced within the cylinder 84 so as to effect .the

forward movement of the piston 82 to the left. Thus, when the handle 88 is moved in a counterclockwise direction as viewed in Figure l, the cylindrical valve 82 is moved so as to effect the automatic and hydraulic actuation of the centerpiece 58, and during the final stage of the movement of the arm 88 the split casing is clamped against the sleeve 65. When the arm 88 is moved in a clock-wise direction so as to shift the valve to the left from the position shown in Figure 2 the valve 92 is moved so as to establish communi- Front carriage construction From the foregoing it will be apparent that work may be convenientl associated with and removed from the main spindle and tail-stock center and I will now describe the structural characteristics of the front tool supporting carriage which I have designated generally by'the numeral i Iii, Figures 2, 4 and 6. This carriage includes a base or frame H2 which is clamped upon and supported by a horizontally disposed cylindrical member or bar Ill. The lower portion of the frame or base H2 is split to permit the same to be clamped in position upon the bar ill by means of suitable bolts Hi. This bar H4 is reciprocable and rotatable within bearings ill and I20, said bearings being located in the main machine frame 34 as clearly shown in Figure 6. One extremely of the bar I i4 is'connected to a piston I22 which is reciprocable-within a cylinder I24. It will be understood that said piston is moved to the left when oil is introduced in the right end of cylinder chamber and is moved to the right when oil is introduced in the left end thereof, Figure 6. The axial movement of the bar Ill serves to move the carriage Ill between'the starting position shown in Figure 1 and the extreme advanced position shown in Figure 2. v

The frame 2 extends forwardly of the machine as shown in Figures 2 and 4 and is supported by means of a screw I30, the lower extremity of which carries a roller I32. This roller I32 rests upon a guide bar I34 which is pivotally mounted at one extremity upon the main frame The anupward movement of the guide bar I24 is limited by an' adjusting screw- I42 carried by a bracket I44. A cross slide I48 is mounted upon the upper portion of the frame H2 and movement of the q slide toward and away from the supported work is occasioned by means of a suitable screw I48 which makes a threaded engagement with the very rigid support for the carriage I I8 and it will be observed that any chips resulting from the engagement of the cutting tool I52 with the work will not come into contact with any of the carriage operating mechanisms. In other words, the guide bar I84 and its associated parts are conipletely shielded beneath the frame H2. The upward movement of the piston I88 causes the front carriage to be swung to the rig-ht, Figure 4, about the axis of the bar II4 so as to carry the tool I52 into operative engagement with the work, the

limit of its swinging movement being determined by the position of the adjusting screw I42 against which the bar I84 is moved. This screw- I42 may be adjusted so that when the carriage reaches the limit of its swinging movement, the tool I52 will be properly positioned for making a cut across the work surface. After the tool has been thus positioned, the bar I I4 is automatically moved to the left 'by the acuation of means hereinafter to be described so that the tool I52 is moved longitudinally of the work from the position shown in Figure 1 to the position. shown in Figures 2, 3

and 4. After the tool has reached the position shown in Figures 2 to 4 inclusive, the piston I38 is lowered to withdraw the tool from operative engagement with the work and the bar II4 is returned to its .initial starting position.

'In the drawings I have shown the bar I84 with its upper surface I54 positioned within a horizontal plane. However, the bar may be inclined when it is desired to cut a taper in the work. The surface I54 of the bar may be configured in various ways to enable the tool I52 to conform to variations in the peripheral contour of the work. Thus, it may be desirable in,certain instances to provide the bar I84 withv angularly disposed surface portions to bring about the desired cross feeding movement of the tool during the longi- 1 tudinal travel thereof. The screw I48 provides va convenient means for making an accurate ad- Justment of the slide I46 along the frame I I2 and a set screw I56 co-operates with clamp screws I58 in properly positioning the tool within the holder I58. The pistons I22 and I38 are operatively connected with an ail pump later to be referred to more in detail, which pump is driven from the same prime mover which actuates the drive shaft connected with the above described spindle.

Rear tool carriage Attention is now directed to a rear tool carriage which I have indicated generally by the numeral I68, Figures 1, 3 and 4. This carriage includes a Justably mounted upon the main frame and includes a cylinder I88 which houses a piston I68 connected to a piston rod I18. The outer extremity of the rod I18 is threaded and secured to the lower extremityof an arm I12 which depends from and is secured to the outer end of the slide I82. Thus, reciprocation of the piston I88 will cause reciprocation of the slide. I62 toward and away from the work. A tool holder I14 is mounted upon the slide I62 and this tool holder accommodates a cutting tool I18 which is adapted to be clamped in position by means of suitable screws I18. By having the rear carriage mounted in the manner described, a very rigid support is provided for the tool I16.

15 As already stated, the rotation of the work as viewed in Figure 4, is clock-wise and hence the a pressure exerted on the tool I16 during its operative engagement with the work is-downward. This downward pressure is effectively counter- 20 acted by the rigidly mounted tool holder, slide, and frame. The tool I16 is employed for making a facing cut across the work as distinguished- The means for automatically controlling .the

movement of the piston I88 will be hereinafter ,described in connection with the description of the oil system. The underside of the slide I62 carries a rack bar I88 and this rack bar meshes with a gear I82, Figures 4 and 11, which is sup- 80 ported by the frame I64. Meshing with the gear I82 is a companion gear I84 which is keyed to a shaft I86. The outer extremity of the shaft I88 is rotatable within a bearing I88 which is formed integral with a housing I88, and secured to the as shaft I86 within the housing is a gear I82. This gear I82 meshes with a rack bar I84 which extends at right angles with respect to the shaft I86. This rack bar I84 is pivotally connected at its opposite extremity with a slide I86, Figures '1, 40-8 and -9 which forms a part of the oil control mechanism about to be described.-

Oil control mechanism This oil control mechanism, Figures 9, 10, and

Figures 22 to 26, inclusive, includes three co-opcrating units namely, a manual control mechanism indicated generally by the numeral I88, a main Ivalve unit 288 and a distributor or orifice valve unit 282. These units operate to control the proper distribution of oil to various moving parts of the machine. and in this connection attention is directed to the diagrammatic representation of the oil system shown in Figure 22. In

this Figure 22 I have shown schematically an. oil 5:, pump which is designated generally by thenumeral 284. In Figure 5 I have shown an elevational' view of this oil pump unit of standard construction. The oil pump per se does not form I a part of the present invention except as it enters into combination with the oil, system which is a part ofthis invention. Therefore I have refrained from disclosing in detail the structural characteristics of the oil pump 284 and it will suffice to say that this pump includes a rotary plunger pump unit 285, having the usual rotor 288 which is provided with a plurality of radially arranged .p'istons 288. This rotor 286 is adapted to be shifted within a housing 2I8 fer the pur-, pose of varying the displacementof oil. When the rotor 288 occupies a central position within the casing 2 I 8 no displacement of the oil will take place but when said rotor has been shifted to one side of the casing as for example by the manipulation of a handle 2I2, oil will be forced outward- 76 ly from acentral pintle 2I4 through a pipe 2I8,

A low pressure gear pump indicated schematically in'Flgure 22 and designated generally by the numeral 2I8 pumps oil from a reservoir 220 and supplies oil at low pressure to the intake side of the rotary pump 205 through a pipe 222. At this point it should be noted that for the purpose of more clearly setting forth the oil system, I

have indicated the high pressure pipe lines, that is, the pipe lines which carry oil from the high pressure side of the rotary pump 205 by means heavy lines and the pipe lines connected with the low pressure gear pump 2 I 8 by means of light lines. The pipe 2 I8 conducts oil from the rotary pump 205 into the main valve mechanism 200.

This main valve mechanism 200 includes a unitary valve 224 which isreciprocable and partia'lly rotatable within a cylinder or casing 228 as clearly shown in Figure 9 and Figures 22 to 26 inclusive. It will. be observed that the valve 224 is formed with a central bore or passage 228 and game three annular peripheral passages 280, 282 and 284. The central passage or bore 228 communicates with a plurality of radially extending passages 288 which are positioned between the annular passages 280 and 282 and also communicates with radial passages 238 which are positioned between the annular passages 282 and 284. Passages 240 serves as a means of communication between the central passage 228 and a portion 242 of the chamber within the valve casing 228. The valve 228 is formed with a reduced section 244 which is reciprocable, within a split bearing 248 and the extremity of this reduced section 244 is enlarged to provide a piston 248. The central bore or passage 228 extends through this reduced section 244 and into the piston 248, said piston being provided with a plurality of reduced passages 250, Figures 9, 13, 14 and 16, which are designed to permit oil to flow from the central passage 228 into a longitudinalpassage 282 i when the piston 248 occupies the position shown in Figures 13 and-l4. The reason for this'construction will be more apparent as the description pro resses.

One extremity of the unitary valve 224 is connected to a rod 254 rotatable within a bracket 218 which is carried by a shaft 288, Figure 10. The lower end of the handle 218 is formed with an arm 282 which is connected to one extremity 01' a link 2.84, the opposite end of said link being pivotally connected with one extremity of a valve 288 of the distributor valve unit282. The shaft 280 carries the pinion -210 and therefore movement of the handle 218 will cause the bar 282 to be shifted. In the drawings I have disclosed the which pipe is connected with the main control valve mechanism 200. Oil which passes through this pipe 282 enters the annular passage 280 and from this point may be distributed through ports 284, 288 and 288 (Figure 11), when the distributor valve 288 occupies the position shown in which is pivotally connected to the free end of a lever 258. This lever 258 has a pivotal mounting 258 and is connected intermediate its ends to one extremity of a bar 280, the opposite extremity-of said bar being pivotally connected to a shifter bar 282, Figures 9 and 10. This shifter bar 282 is reclprocable within spaced guides 284 and 288 which form a part of the manual control mechanism I88. The underside of the shifter bar I82 is formed with rack teeth 288, Figure 10, which mesh with a driving pinion 210 and the outer extremity of the bar 282 carries a vertically disposed pin 212 which is secured in position by means of a set screw 213. Reciprocation may be imparted to the shifter bar 282 by means of dogs 214 and 218 which are adjustably m'ountedupon the slide I88. The dog 218 is adapted to engage the pin 212 when the slide I88 is moved in response to the rearward travel of the slide I82 of the rear carriage I80. .Likewise, when the slide I82 is moved forward, movement is imparted to the slide I88 so as to carry the dog 214 into operative association with the pin 212. The functioning of these dogs will be more apparent after the oil system has been described more in detail.

The manual control mechanism I88 whichis also designed to impart reciprocating movement to the shifter bar 282 and consequently to the unitary valve 224, includes a manual control lever Figures 9, 10 and 22. Needle valves 800, 802 and 804 serve to control the passage of oil through these ports which thus form adjustable restricted orifices, and these valves are respectively connected with pipes 808, 808 and8I8 as diagrammatically shown in Figure 22. Interposed between the pipe 8I0 and the needle valve 804 is a valve 8 I 2 which is operated in timed relation with respect to the movement of the slide I88 to open and close the oil circuit at this point. If the valve 288 is shifted to the left, Figure 10, in response to the swinging of the handle 218 to the right, the ports 284, 288 and 288 will be closed, thereby permitting unrestricted passage of oil from the annular passage 280 through by-passes 8 associated with each needle valve. In other words, by shifting the valve 288 to the left, Fig.' -10, (right in Fig. 20), increased displacement ofthe oil into the pipes 808. 888 and 8I0 may be .pbtalned. These pipes are respectively con nected with the vertical front carriage cylinder I40, the rear carriage cylinder I88 and the hori- -zontal front carriage cylinder I24 as clearly shown in Figure 22.

Manual operation of oil system Before describing indetail the manner in which the operation of my improved machine is auto matically controlled, 1' will trace the various oil circuits disclosed in the diagrammatic representations in Figures 22 to 26 inclusive. Figure 22 I have shown the main unitary control valve 224 in its neutral position. In this position oil is distributed from the gear pump 2I8 to the rotary pump 205 and then through the pipe 2I8 into an annular port 8 I 8 which at this stage communicates with the central bore or passage .228 through the radial ports 288. Oil from the passage 228 passes through the ports 240 and thence into the chamber section 242. This chamber 242 communicates with the low pressure gear pump 2I8 through a pipe 8I8. From the pipe 8I8 the I will hereafter refer to as the rapid approach position. The shifting of this control lever causes the main valve- 224 to be moved to the position shown in Figure 23. In this position oil from the pipe 218 passes through the annular passage 299 and thence through the pipe 292 which communicates with the distributor valve mechanism 292. It will also be noted that when the valve 224 occupies the position shown in Figure 23, the annular chamber 294 establishes communication between the central passage 228 of the valve and a low pressure pipe line 929 which is connected with a cylinder 922, Figure 22. The displacement of the oil through this pipe 929 causes a piston 924 in thecylinder 922 to be urged to the left, thereby rocking the rotor 296 to its extreme position of displacement within the'casing 219. This is the position of maximum displacement and thus it willbe clear that this in- I The valve 912 will occupy a position shown by the dot and dash lines in Figure 22, thereby prevent- Figure '22 so as to permit the passage of oil through the pipe 919 and this passage of oil will effect the movement of the horizontal front carriage piston 122 to the left. piston 122 causes the front carriage to be fed longitudinally of the work" at a feeding speed. At

this period further upward movement of the piston 199 will be-prevented by reason of the engagement of the guide bar 134 with the adjustable screw or stop I42, Figure 2. The rear carriage piston 168 will be moved forwardly at a feeding speed. As is obvious, the volume diiferential between the fluid displaced by the pump during feed, at the setting of the handle 212, and that transmitted through the needle valve orifices, is diverted-through relief valve 458. As one carriage completes its feeding travel, and during the completion of the feeding movement of the other, the volume of diversion is of course increased. The handle 212 may be employed to control the pumping rate so as to avoid excessive diversion, which would tend toward excess heating of the fluid medium.

If, upon the completion of the-forward stroke of the cutting tools, the control lever 219 is moved to its neutral vertical position, the main control I valve 224 will occupy the position shown in Figmg oil from passing through the pipe 319 which is connected with the horizontal front carriage cylinder 124.

The introduction of oil within the cylinders I49 and 166 will cause a rapid swinging move ment of the front carriage with its cutting tool 162 toward the work and the rapid sliding advancement of the rear carriage cutting tool 118 toward the work. This movement is what I have referred to as the rapid approach movement. As the piston 19B is moved upwardly, oil from the advancing side thereof passes through a pipe 928 and oil from the advancing end of the piston I69 passes through a pipe 928, said pipes having a common connection with a return pipe 939 which communicates with an annular port 992 provided in the casing 226. This port 992 communicates with the central passage 228 which, at this'time,

is connected to the low pressure side of the system through the pipe 218.

Assume now that the handle 218 is moved to its feed position as indicated on Figure 9. This and in this position the connection between the ure 9. As already described in connection with the starting or neutral position of the main control valve as shown in Figure 22, oil supplied through the pipe 216 will then pass through the radial ports 296, the ,central passage 229, the chamber 242 and thence into the return low pressure pipe 918. For the purpose of more clearly disclosing the automatic control features later to the described, I have shown the control mechanisms in this neutral position in Figures 7, 9 and 10,'-and obviously the various operating pistons will at this time be positioned at the limit of their advancing stroke in readiness to be reversed.

Assume now that the cutting tools have reached the limit of their advancing movement as above set forth and that the control lever 218 has been swung from the neutral position to the xtreme position to the right, Figure 9, which I will hereinafter refer to as the rapid reverse position.

, When the lever occupies this position the main pipe 929 and the low pressure side of the system I the rotor 296 to be moved to its'normal position of displacement within the casing 219. A normal feeding displacement of oil as determined by the setting of handle 212 will then pass through the pipes 216 and 292' and thence through the needle valves into the pipes 996, 998 and 919. At this time the valve 912 of the distributor mechanism will be positioned as shown by the solid lines in valve 224 will occupy the position shown in Figure 25. In this position the pipe 929 is again connected with the low pressure sid of the system, thereby eifecting the rocking of the rotor 296 to the left as above described. Oil which is thus displaced at an"increased rate through the pipe ,216, enters the annular passage 292 and then passes outwardly through the pipe 999 which communicates with the cylinders 124, 149 and 166 so as to cause the quick reverse movements of the pistons 122, I98 and 168. This serves to quickly carry the tools out of engagement with the work and also serves to eifect rapid-reverse travel of the piston I22 which is connected with till: reciprocatory bar 114 of the front carriage If it is desired to eflect ,the reverse movement of the front carriage 119' longitudinally of the work and the rearward movement of the carriage slide 162 at feeding speeds, it is only necessary to move the handle 218 to the reverse feed position as indicated on Figure 9. This will cause the-main control'valve 224 to occupy the reverse feeding position shown in Fi ure 26. In this position the pipe 929 will be cut oil from the low pressure side of the system, thereby automatically causing the rotor to assume the position of normal displacement and the oil will be dis- Movement of the asvaoos placed throughthe pipes 2 II and 838 at a normal feeding rate. When the tool carriages have been returned to their initial starting point, the lever 218 is moved to its neutral position, thereby moving the main control valve to the position shown in Figure 22.

It is also to be noted that the tail-stock control cylinder 84 is operatively associated with the low pressure side of the above describedoil system through the agency of a pipe line 336, Figure 22, which is connected between the port I08 and an annular port 338 provided in the main valve casing 226. This annular port communicates with the low pressure side of the oil system through the radial ports 288 and the central passage 228 as clearly shown in the drawings. The port I82 of the tail-stock cylinder is connected by means of a suitable pipe line 348 to the reservoir 228.

Description of automatic oil control After the work has been positioned between the work spindle and the tail-stock center, and the operator has properly adjusted the positions of the tools I52 and I16 with respect to the work, the operator moves the handle 218 to the rapid approach position, that is, to the extreme left, Figure 9. As already described, this causes a sudden upward movement of the front carriage piston I38 anda sudden forward movement of the rear carriage piston I68. The upward movement of the piston I38 causes the guide bar I34 and the roller resting thereon to be elevated, thereby causing the tool I52 to be carried into proper operative relation with respect to the work which, at this time, is rotating in a clockwise direction as above set forth. The limit of the upward movement of the bar I34 is-determined by the position of the adjustable screw or stop I42.

As the rear carriage slide I62 is advanced in response to the movement of the piston I68, the

meshing gears I82 and I84, Figures 4 and 11, are rotated, thereby causing rotation of the, gear I82 carried by the shaft I86. This causes the rack bar I94 and the slide I86 connected therewith to be moved to the left, Figures '1 and 8. As the slide I86 is moved, the dog 214 is eventually carrled into engagement with the pin 212 carried at the outer extremity of the slide bar 262. This causes the slide bar to be shifted to the right from its extreme left position, which position has hereinbefore been referred to as the rapid approach position of the lever 213. The shifting of the bar 282 causes the main control valve 224 to be shifted to the right, thereby causing the same to occupy the position shown in Figure 24. This position has been referred to as the feeding position, that is, the position which causes oil to be displaced from' the rotary pump 205 at a' normal feeding rate. It is also to be noted that during the forward movement of the slide I96, a dog 342 is carried into engagement with an arm 344 of a bell-crank 848, Figure 9, and this bellcrank is connected with the valve II! of the distributor mechanism by means of a link 348. The engagement of the dog 342 with the bell-crank. causes the valve 8I2 to be moved to the position in Figure 8, thereby establishing communication between the pipe I! and the needle valve port 288, Figure 17. This causes the horizontal front carriage piston I22 tobe moved to the left, Figure 8, thereby imparting a feeding movement to the frxoirsit tool carriage longitudinally of the work a Asthe tool I18 reaches the limit of its forward movement, a lug 388, Figures 1 to 10 inclusive and Figure 12, is carried into engagement with a pin 352 which is carried by a housing 354'formed j integral with the upper arm 356 of a lever mechanism 388. A coiled spring 388, Figure 12, is lodged within the housing 384': and counteracts the movement of the pin to the left in response to the engagement therewith of the lug 358. The outward displacement of the pin 352 is prevented by a collar 362. The lever mechanism 358 is formed with a depending arm 364 and. the extremity of this am is formed with an aperture 386 which receives a pin 368 carried by a slidablc shaft 318. This shaft is slidably mounted in suitable brackets 312, Figures 7, 9 and 12,- and ,a coiled spring 314 is interposed between one of the brackets 312 and a collar 316. This spring serves to constantly urge the shaft 310 to the left, Figures '7 and 12. The'opposite extremity I of the shaft 318 is pivotally connected to the outer end of an arm 318 carried at the upper extremity of a vertical shaft 388. The lower extremity of this shaft carries another arm 382 which is adapted to be engaged by a lug 384,

Figures 7 and 9, which is carried by'a ring 386 mounted upon the cylindrical front carriage bar When the bar 4 approaches the limit of its advancing movement, the lug 384 is carried into engagement with the arm 382 and this causes. the shaft 31li.to be moved to the right,,Figures 8 and 12, against the action of the coiled spring 314. The movement of the arm 356 of the lever mechanism 358 to the left, Figure 12, in response to the engagement of the lug 356 with the pin 352 and the lug 384 with the arm 382 causes a link 388 to be moved to the left. The extremity of this link is provided with a slot 390 which receives a pin 392 carried by a valve oscillating guide 384, Figures 9, 12 and 13. This valve oscillating guide 384 extends within the casing 226 of the main valve unit 280 and is keyed to a reduced end sect on 386 formed integral with the v'alve 224 as by means of a radial lug 388. Movement of I the link 388 to the left causes the valve oscillating guide 394 tobe rotated in a clockwise direction to the position shown in Figure 12. In this position the reduced radial passages 250 of the valve piston 248, Figures 13 and 14, establish communication between the central bore or passage 228 and the passage 252. The passage 252 communicates with a section 488 of the valve chamber and thus oil introduced within this section dllll will cause an unbalancing of the main valve 224 so as to efiect the movement thereof to the right,

Figures 9 and 13.. The valve 224 is thus carried to the reverse position shown in Fi ure 25 and as hereinbefore described. the valve in this position serves to effect the rapid reversal of the pistons associated with the front and rear tool carriages. j

Referring again to the lever mechanism 358 that this mechanism in co-cperation with the lug 366, carried by the slide I36 and the lug 364 on the ring 366, operates to prevent the reversal of the machine until all of the cutting tools have completed their advancing stroke. In other words. the reversing of the machine is controlled by the lug which is last to be carried into operative engagement with the lever mechanism366. Consider for example that the front carriage tool I52 completes its cutting stroke after the 'rear carriage tool I16 has completed its stroke. In this case the lug 356 will engage the pin 362 before the lug 384 engages the arm 362, Figures 7 and 12. The engagement of the lug 356 with the pin 352 causes the arm 356 to be swung slightly counter-clockwise as seen in Fig. 12, the pin 366 normally being at the right end of slot 366. This carries the left surface of the aperture 366 into engagement with the pin 366 carried by the shaft 316. The spring 366 associated with the pin 362 is lighter than the spring 314 carried by the shaft 316 and hence further movement of the arm 366 counter-clockwise is prevented. The movement experienced by the link 366 in response 'to this initial swinging of the arm 356 causes -rotation of the valve oscillating guide 394 but of the valve guide to the position shown in Figure 14. If the front carriage tool reaches the limit of its forward stroke ahead of the rear carriage, it will be apparent from the above explanation. that suflicient rotation will not be imparted to the main valve 224 until the lug 366 is moved into engagement with the resiliently mounted pin 362. In other words, by having suflicient play with a pipe 464 which connects with the oilreser- 'voir 226. Figure 22. I

Drive mechanism disclosed a conventional prime mover in the form of an electric motor 466, Figures 1, 3 and 16. which is adiustably mounted upon the machine bed by means of screws 461. The drive shaft of this motor is connected to a driving sprocket between the pin 366 and the wall of the aperture 366, a slight rotary movement is imparted to the valve 224 by the first lug to reach the limit of its advancing movement and final movement is imparted when the last lug completes its movement.

In Figure 13 I have disclosed an enlarged view of the piston end of the main valve and have shown the piston 246 in its advanced position. Immediately after the piston has reached this position, the pistons associated with the front and rear carriages experience a reverse movement and this carries the lugs 356 and 364 away from the pin 352 and the arm 362 respectively, thereby permitting the spring 314 to move the lever mechanism 356 so as to rotate the valve 224 from the position shown in Figure 14 to the pressure relieving position shown in Figure 16. The slot 396 provided in the link 366, delays the return of the valve 224 to its pressure relieving position shown in Figure 16, thereby insuring the complete forward stroke of the valve within its casing. When the valve 224 has been thus oscillated, communication between the central passage 226 and the passage 252 is interrupted, and communication is established between the passage 252 and an annular passage 462, Figures 9 and 16, so as to relieve the fluid pressure and bring the valve member into fluid pressure balance. This annular passage 462 communicates 326 connected to the rear carriage cylinder I66.

466 of the conventional oil pump unit 264 by means of a silent chain 466, Figs. 3 and 5, and is operatively connected with a sprocket 416 by means of a silent chain 2. The screws 46'! serve to enable the motor to be adjusted with respect to the. main drive shaft and oil pump. The sprocket 466 is laterally adjustable by means of a swinging bracket 4| I. The sprocket H6 is mounted upon the hub of a clutch element 4,

which 'element is lo'oseiymounted by means of ball bearings 4| 6 upon the main drive-shaft 66. This drive-shaft 66 is supported at its outer extremity by means of a suitable ball bearing 6 and carries a pulley 426 which may be used for driving a cooling pump not shown. The clutch mechanism which I have designated generally by the numeral 422 may be of any practical design and in the present embodiment of the invention I have shown a clutch of the disctype. A clutch element 424 which is axially movable in response to the movement of actuating arms 426, Figure 18, serves to connect and disconnect the power supplied from the prime mover. 'I'hemovement of these arms is occasioned in response to movement which is imparted to the collar 426 supported by members 436, Figure 19. These members 436 are connected to the outer extremities of spaced arms 432 which extend outwardly from and are formed integral with a vertical sleeve 434 mounted upon a shaft 436. The sleeve and shaft are supported by suitable brackets 436 which extend outwardly from a frame 446, Figures 1, 3 and 18, which is secured to the side of the head-stockframe 32. The change gear 66 is mounted at the outer end of the main drive shaft 66 and this meshes with the companion change gear 66 which in turn drives the pinion 64, said pinion meshing with the main spindle drive gear 52. From the foregoing it will be apparent that the clutch mechanism 422 serves to control the delivery of power from the prime mover to the work supporting spindle.

, Hydraulic clutch control I provide means for hydraulically and automatically controlling the actuation of the clutch ures 1, 19 and 26. A piston 444 connected to a piston rod 446 is reciprocable within the casing 442. Oilconducting pipes 446 and 446 are connected to opposite ends or the cylinder chamber and as clearly shown in Figure 22, the pipe 446 forms a branch of the high pressure pipe line 366 and the pipe 446 forms a continuation of the pipe The outer extremity of the piston'rod 446 is connected to the free end of an arm 466 mounted upon the upper end of the shaft 436 and it will thus be apparent that when oil is initially displaced through the pipe line 366 as above described, this displacement will cause the piston 444 to be urged to the left, Figure 20. This causes asvaeoa tion with the rotating work. The forward movement of the piston Ill causes the rear carriage the vertical mam to be rotated in a direction so as to carry thecollar 426, Figure 16, intoengagement with the arms 426 which in turn operate the clutch mechanism so as to positively con-,1

nect the main drive shaft 64 with the source of power. This causes rotation of the work spindle I8. Thus, when the operator moves the operating handle 216 to the rapid approach or starting position as above described, the work spindle will automatically be connected to the source of power supply. When the flow of oil through the pipes 366 and 326 is reversed, a reversal of the flow of oil will also be experienced in the pipes 446 and 446 connected to the cylinder 442, thereby causing the piston. 444 to be moved to the right, Figure This effects the immediate disengagement of the clutch. In other words, when the tools have reached the limit of their operative position the oil, pump 266 is conditioned for a feeding displacement of the oil and the distributor valve 266 is moved to a position whereby communication with the non-adjustable by-pass ports is interrupted 'andcommunication is established with the adjustable or needle valve ports. During the movement of the slide I66, the dog 342 engages the arm 644 of the bell-crank 346, Figstroke and the machine is thrown into reverse,

the source of power supply is disconnected from the work supporting spindle. In some instances as'for example during reverse feed it may be desirable to constantly maintain the driving connection between the source of power and the work spindle, and in such instances it is only necessary to tighten a set screw 462, Figure 20, and thereby ure 9, and this conditions the valve 6I2 so as to establish communication between the needle valve 264 and the pipe SIII which connects with the front carriage cylinder I24. Thus, feeding movement longitudinally of the work is imparted to the front carriage in response to the movement of the pistonlzl and feeding movement trans-' versely of the work is imparted to the rear carsecure the piston 444 in position at the left end of the cylinder. 1 I

Statement of operation The operator mounts the work upon the face plate 46 of the work spindle and by moving the tailstock control lever 68 from the position shown in Figure 1 to the position shown in Figure 2, oil is introduced within the cylinder 64 so as to cause the center-piece 66 to be moved into association with the work and during the final move.- ment of the handle 86, the sleeve 66 is clamped in position within the tail-stock casing 64. The front tool carriage Illl and the rear carriage I66 now occupy the positions shown in Figure 1. After the tools I52 and I16 have been properly positioned in their respective holders, in the described cycle of operation the operator moves the lever 216 to its extreme left position which has heretofore been referred to as the rapid approach position. This causes the main control valve 224 to be moved to the position shown in Figure 23 and the main distributor or orifice valve 266 is with the front carriage cylinder I46 and the rear The piston 444 associated carriage cylinder I66.

with the clutch mechanism is simultaneously riage tool.

When the cutting tools approach the limit of their feeding stroke, the lug I60 carried by the slid I96 approaches the pin I62 and the lug 384 carried by the ring 666 approaches the arm 382. The engagement of these lugs in the manner described causes the actuation of the lever mechanism 356 and this effects the oscillation of the main valve 224. This oscillation is effected in response to the tool which is last to complete its forward cutting stroke. The oscillation of the valve 224 causes the pressure at opposite ends thereof to become unbalanced and said valve is automatically and hydraulically moved from its feeding position shown in Figure 24, past the neutral position shown in Figure 9 and thence to its rapid reverse position shown in Figure 25. The oil pump is now conditioned for maximum displacement, thereby causing the tool carriage pistons and the clutch control piston to experience a sudden movement in the reverse direction.

As the tool carriages reach their initial or starting position, the dog 342 engages an arm 454 of the bell-crank 346 and this closes communication between the pipe line 3H) and the main distributor valve 266. contemporaneously with the completion of the rearward movement of the carriage I66, the lug 216 carried by the slide I66, Figure 9, is carried into engagement with the pin 212 carried'by the slide bar 262'and this causes said bar to be moved to the left, thereby moving the valve 224 to its neutral position shown in Fi ure 22.

By rotating the tail-stock handle 88 from the position shown in Figure 2 to the position shown in Figure 1, the valve 92 associated with the tailstock is moved so as to efiect the automatic retraction of the center-piece 68, thereby enabling the operator to remove the work supported by the spindle 38. The operator then inserts another article between the head-stock and tailstock and moves'the control lever 216 to its rapid approach position, thereby conditioning the machine to automatically perform a complete cycle of operation as above described.

Referring to Figure 22, it is to be noted that I provide the relief valves 458 and 466 in the high pressure and low pressure pipe lines. The valve '456 is connected with the high pressure pipe 2IG

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