USRE20974E - Metal working apparatus - Google Patents

Description

Jan. 10, 1939.

P. R. GUIRL ET AL METAL WORKING APPARATUS 10 Sheets-Sfieet 2 Original Filed Nov. 24,- 1933 E 'ZZ-A I @w W 9 A Jan! P. GUIRL ET AL ,9

METAL WORKING APPARATUS Original Filed Nov. 24, 1933 10 Sheets-Sheet 3 .EUJ/QIZZOT'S.

' .fahzz 3. Barnes, Dead yfiqp e Barnes, his ezecuzh'z Paul JP. Guir'l,

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- P.'R. GUIRL ET AL. METAL WORKING APPA ATUS Original Filed Nov. 24, 1953 Wwm WNW ww WQE l in the production of exceptionally large and' Reissued Jan. 10, 1939 UNITED STATES METAL WORKING APPARATUS Paul R. Guirl, Rockford, Ill., and John S. Barnes, deceased, late of Rockford, 111., by W. F, & John Barnes Company, Rockford, Ill., assignee Original No. 2,030,562, dated February 11, 1936,

Serial No. 699,548, November 24, 1933. Application for reissue February 10, 1938, Serial No.

This invention relates generally to metal working apparatus, and more particularly to apparatus for cutting tubes or pipes.

During the past few years large quantities of oil and gas from the fields of production have been transported over an extensive system of pipe lines. The consumption of natural gas in homes, factories, and the like has been a stimulating influence in leading to the adoption of pipe lines as an eflective means of conveyance. The pipes or conduits used for such purposes are unusually large, and consequently very heavy. As a result, the steel industry has found it necessary to devise new methods and design new machinery to adequately, economically, and quickly supply the present demand. The present invention has a very practical application in the field of pipe or conduit production, andparticularly heavy tubing. Due to the weight and bulk of the tubing, it has been impracticable to employ cut-off'machines of the type wherein the work is rotated and a cutting tool is held stationary. Tubing of the type mentioned above is not always produced in absolutely straigi .t lengths, and hence difl'lculty arises in mounting such tubing in a. rotary work support or chuck. It will be apparent that if a length of tubing is not straight, and one end thereof is mounted in a rotary chuck for the purpose of cutting off a section of the tubing, the free end will, during rotation, experience a decided whipping action. It is, therefore, one of the important objects of the present invention to provide a machine wherein the above mentioned and other difiiculties are completely overcome, and whereby piping or tubing may be machined, cut off, chamfered, and the like in a very economical and practical manner.

More specifically, the invention contemplates a machine wherein the tubing is accurately clamped in position against rotation, and a plurality of rotary cutters are employed to perform the required machining operation.

Still more specifically, the invention contemplates a machine wherein the rotary cutters are adapted to shift in a radial direction toward and away from a rigidly supported work piece or tube, and this arrangement is combined with an efficient control mechanism for automatically governing the movement of the tools.

Another object of the invention is to provide a practical and efficiently operable work holder or'support which is easily adjustable to accommodate various sizes of tubing, said support being so arranged as to obviate the necessity of disassembling or changing any of the machine parts to accommodate various'sizes of tubes.

Still another object of the invention is to provide' in a machine of the type set forth above,

28 Claims. (01. 82-20) means for controlling the speed of radial movement of the tools in such a manner that said tools may be shifted at various speeds, depending upon the nature of the work to be performed.

A further object of the invention is to provide in combination with the rotary cutting mechanism set forth above, hydraulic actuators for efiecting reciprocation of tool slides together with valve means for governing the length of stroke of said slides.

Still another object of the invention is to provide a machine tool of the type mentioned above, wherein the tool slides are radially reciprocable and adapted to rotate about the axis of a supported work piece or pipe, said work. piece being supported and clamped in position and power means being provided to shift the work piece into position to be acted upon by the tools, another mechanism being provided for receiving and holding the severed portion of the work piece.

A further object of the invention is to provide improved means for chamfering either the internal or external margin of a tube or conduit, this being accomplished by securing the work against rotation and moving a plurality of chamfering tools about the axis of the work piece.

In addition to the above mentioned 'obiects and advantages, the present invention contemplates the provision of a safety feature to insure continued operation of the machine, and to this end a safety feature is incorporated whereby the driving motor for the machine automatically stops in the event that the pressure in the lubricating system drops to a. predetermined point; in other words, when the lubricating system is not functioning properly, the machine cannot be started.

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 a side elevational view of a machine which is representative of one embodiment of the invention;

Figure 2 is an enlarged fragmentary planview of the .control valve mechanism and dogs for timingly controlling the fimctioningof said valve mechanism;

Figure 3 is an end elevational'view of the machine shown in Figure 1, said view being taken substantially along the line 3-3 of Figure 1;

Figure 4 is a fragmentary detail central sectional view of the valve mechanism which preventsthe prime mover or motor from starting unless s lili cient oil pressure for lubrication is established;

Figure 5 is a fragmentary vertical sectional view of the machine taken substantially along the line 5-4 of Figure 3, with a tubular work piece in position to be acted upon by the rotary tool cutting mechanism;

Figure 6 is a-horizontal transverse sectional view of the machine taken substantially along the line 6-6 of Figure 3, the tubular work piece being removed in order to more clearly disclose parts otherwise hidden;

Figure 7 is an enlarged horizontal sectional view of the mechanism for moving a pipe or tube into position to be cut, said view being taken substantially along the line |-i of Figure 1;

Figure 8 is a fragmentary detail sectional view of the mechanism for adjustably supportingthe work or pipe, said view being taken substantially along the line 8-8 of Figure 9;

Figure 9 is a vertical transverse sectional view of the machine taken substantially along the line 99 of Figure 5;

Figure 10, is an end view of the machine as seen from the right of Figure 1;

Figure 11 is a vertical sectional view of the mechanism for moving the pipe into position, said view being taken substantially along the line ll-ll of Figure 1;

Figure 12 is. an enlarged transverse sectional view of the mechanism for clamping the portion of the work extending beyond the rotary cutting mechanism, said view being takensubstantlally along the line l2-i2 of Figure 1:

Figure 13 is an enlarged detail sectional view of one of the tool holding devices, said view bein taken substantially along the line lS-ll of Figure 3;

Figure 14 is afragmentary enlarged perspective view of one of the tool holding slide structures shown in operative association with its companion actuating bar Figure 15 is a semi-diagrammatic disclosure of the hydraulic control and the mechanism for operating the rotary cutter mechanism:

Figure 16 is an enlarged plan view of a modifled tool holding device which is designed to support a chamfering tool;

Figure 17 is a front elevational view of the device shown in Figure 16;

Figure 18 is an end view of the device shown in Figures 16 and 17, said view being taken from the left of said figures Figure 19 is a plan view of a modified tool holding device arranged tosupport. a tool designed for internal chamfering work;

Figure 20 is a front elevational view of the device shown in Figure 19; and

Figure 21 is an end view of the device shown in Figures 19 and 20, said view being taken from the left of said figures.

Referringnow to the drawings more in detail wherein like numerals have been employed to designate similar parts throughout the various figures, it will be seen that a machine embodying features of the present invention includes a base 36. Extending upwardly from the left portion of the base 30 (Figures 1 and 5) is a frame or housing 32, which provides the main supporting structure for a rotary tool cutting mechanism designated generally by the numeral 36. Extending upwardly from the right side of the base 36 is a frame structure 36, which provides the main support for a work holding device designated generally by the numeral 36 (Figures 5 to 8, inclusive). The frame 66 also provides a mounting for a mechanism 40, which forms the driving coupling between hydraulic mechanisms 42 and radially shiftable tool holding devices I, later to be described, said devices being radially slidable at the forward side of the rotary cutting, mechanism 34. The frame 36 alsopro'vides the support for a prime mover or electric motor 46 which serves to impart rotary movement to the tool holding devices 44. A work piece such as a pipe 46 is moved into operative association with the rotary cutting mechanism 34 and the work supporting mechanism 36 through the agency of v Rotary cutting mechanism Reference having been made in a general way to the main operating structures of the machine, a detailed description of the rotary cutting mechanism 34 will now be given. This mechanism includes a rotary member or drum 54 supported by anti-friction bearings 56 carried. by the frame 32 (Figure 5). The forward end of the driving drum 54 is apertured at 58 to receive Ithe work piece 68 and also carries a mounting plate or disk 66, which plate is also apertured to receive the work. The tool holding devices 44, previously referred to, are supported upon the outer face of the mounting plate 60 as clearly indicated in Figures 3, 5, and 13. There are in all six tool holding devices radially disposed and equally spaced along the surface of the plate 60, and each of these devices 44 includes a slide 62 which is adapted to be radially reciprocated along the face of the plate 60 in response to longitudinal movement of a companion bar 64. This bar 66 is provided with a longitudinally key 66 to prevent the bar from rotating about its axis. The oppositely disposed surface of said bar is provided with teeth 68 which mesh with companion teeth l6 in the slide 62. These teeth are so disposed that when longitudinal movement is experienced by the bar, radial movement will be transmitted to the slide 62. It will be seen that the bar 64 is companion to each of the slides 62, and that these bars are slidable within bearings 12 formed on the plate 66 and bearing sections 14 provided along the periphery of the drum 54 (Figure 6). Each of the slides 62 carries a block 16 which is adapted to be adjustably secured upon the slide 62 by means. of suitable bolts 18, which engage a gib 19 at their inner ends. It willbe noted that the block 16 is provided with a plurality of grooves 80, and

the slide 62 is provided with a plurality of similar grooves 62. In order to adJust the position of theblock 16 .upon the slide 62, it is only necessary to loosen the bolts 16, remove a key 84, and shift the block 16 until the desired complementary grooves are brought into registration. The key 64 is then reinserted and the bolts 16 tightened.

A cutting tool proper 66;is adapted to be clamped a may be tightened. .It will also be noted that gibs 96 and I66 carried by the member 66 serve to accurately guide the slide 62 (see Fig. 13). Thus it will be apparent that when the bars 64 experience longitudinal movement to the right (Figures 5 and 6) the tool holding device 44 will be shifted inwardly so as to bring the tools 86 into operative association with the periphery of the work 48. By mechanism, later to be described, the initial inward movement of the tool holding devices is relatively rapid, and, as the cutting' Mechanism for rotating tools The mechanism for imparting rotation to the tool driving drum 54 is driven through the agency of the prime mover or motor 46. This vmotor may be a single speed, multi-speed, or

D. C. motor of suitable design. A gear I02 connected directly with the shaft of the motor 46 meshes with a gear I04 (Figures 1 and 15). The gear I04 transmits power to a pair of pick-off gears I06 and I08. The size'of the pick-off gears will obviously be determined by the speed at which tools are desired to be rotated. The pickoff gear I08 is coupled with a smaller gear II 0 which meshes with a gear II2. This gear II2 meshes with a large annular gear II4 mounted upon the periphery of the hollow tool supporting member or drum 54.

Mechanism for radially shifting tool holders The mechanism for imparting longitudinal movement to the bars 64, and ccnsequently radial movement to the tool holding devices 44, includes an annular member II6, which is connected with the ends of the bars 64 by means of suitable clamping nuts NB. This member II6 forms a unitary coupling for the inner ends of the bar 64 and is freely rotatable within a pair of symmetrical stationary members I20. These members I20, at. diametrically opposite points, are coupled with piston rods I22 (Figures 6 and 15).

clamp the members I20 'to the piston rod. Positioned within the members I20 is an anti-friction bearing structure I26.. Thisstruct-ure I26 includes a pair of outer annular race members I28 (Figure 6), which cooperate with a central. race member I30 to secure ball bearings therebetween. By this construction, the annular member H6 is free to float within the members I20, and, in response to longitudinal movement of the piston rods I22, radial movement will be transmitted to the tool holding devices 44 through the agency of the annular member H6 and the bars 64 coupled therewith. One extremity of these piston rods I02 is slidably supported within bearings I32 mounted upon the outer surface of the upright frame section 32. The opposite extremity of each piston rod I22 connects with a piston I34 reciprocable within a cylinder I36, and the movement of the piston within said cylinder is controlled by a valve mechanism I38, later to be described.- It will suflice to say at this point that the position of the valve mechanism governs Each of the piston rods I22 is threaded to receive a clamping nut I24 which serves to' the speed and direction of travel of the pistons In order to rigidly support the annular members I20 in proper position within the frame structure, four guide bars I40 are employed. These bars are threaded to receive clamping rings I42 which are designed to be firmly tightened against the outer surfaces of the annular members I20 by any suitable tightening means such as a spanner wrench (not shown). These clamping rings or collars I42 serve to securely clamp the members I20 together in a fixed position upon the bars I40. The inner extremities of the bars I40 are reciprocably mounted within the frame 32 and the outer extremities thereof are reciprocable within bearing sections I44 of the upright frame section 36. In this manner the rings or annular members I20 are accurately guided withinthe frame 36 when they are shifted by the hydraulic actuators 42,

Attention is directed to a,rack bar l46 which traverses the'lower portion of the machine structure and meshes with vertical shafts I48, as clearly indicated in Figures 6 and 10. These shafts are provided with intermediate teeth I50, which mesh with companion rack teeth I52 provided on the bars I40. This rack bar arrangement serves as a compensator for the hydraulic actuators 42. It sometimes happens that one of the tools will start to cut in advance of the others due to the uneveness of the work piece 48, and this would have a tendency to impose an unbalancing action on the actuators and cause a strain which would tend to force the structure out of alignment. The above mentioned rack I and pinion construction serves as an equalizing means which precludes the introduction of such strains.

Work carrier Attention is now directed to the manner in I which the work piece 48 is supported by the carrier mechanism 38 and is secured against rotation within the machine during the cutting operation. This carrier mechanism includes a hollow bracket or frame I54. This frame I54 includes a flanged section I56, which is positively secured to the frame section 36 (see Figures 5 I will be apparent that the cradle I66 provides a rest or support for the'lower surface of the work 48. Thus, the weight of the work piece 48 and the cradle I 66 is carried by the cam members I62, which are, in turn, mounted upon the carrier I54. The cradle I66 is secured against longitudinal movement by an abutment plate I68 at one extremity and an abutment plate I10 at the opposite extremity (Figure 8).

' The cam members I62 are secured. to a bar I12 connected with a'screw shaft I14. The screw shaft I14 can be shifted longitudinally by turning the outer squared end of a shaft I16 (Figures 8 and 10), which shaft is rotatable within suitable .bearing structures I18. These bearing structures I18 include a housing I and a pair of antifriction thrust bearings I02, which are worm wheel of gear I66 The gear I66 having a threaded mounting upon the shaft I14, will cause longitudinal movement of the bar I12 when rotation is imparted to the squared end of the shaft I16. In this manner the cradle or work holding device I66 may be raised or lowered to accommodate various sizes of tubes. By merely rotating the shaft II6 so as to cause the cam members I62 to shift to the right (Figure 8), the

cradle I66 is elevated. This provides a very rigid and radially adjustable support for the work or tube 48.

Work clamping device After, the work piece has been positioned by the cradle I66, a clamping member I66 is urged downwardly against the upper surface of the work, as clearly indicated in Figure 5. This clamping member I86 is pivotally supported at one end of a lever I96. This lever I96 is pivotally supported upon a bracket I92, and the opposite extremity of the lever I96 is pivotally connected with a piston rod I94 of a fluid actuator I96. This fluid actuator may be of any conventional design, and may be either hydraulically actuated or air operated. It will sufilce to say that when the piston I96 within the cylinder 266 of the actuator I96 is urged upwardly, the member I66 is firmly clamped against the upper surface of the work 46.

It will be apparent from the foregoing description that the cradle I66 and its associated parts cooperate with the clamping member I66 to provide a chucking mechanism, namely, a mechanism which properly centers the work with respect to the rotary tools 66. While the cradle does not function to clamp the work in place, it does supply the undersupport for the Work when the member I66 is clamped against saidwork. Thus, the tubular work piece is firmly secured against rotation within the machine during the operative functioning of the tools 86.

Work shifting mechanism The work shifting mechanism 56 shown more clearly in Figures 1, 7, and 11, includes a suitable base 262, which carries at its upper end a pair of oppositely disposed symmetrical roller supports- 264. Rollers 266 comprising oppositely disposed cone sections are adapted to frictionally engage the outer surface of the work 46, as clearly indicated in Figure 11. Rotation is imparted to these rollers 266 through the'agency of a prime mover or electric motor 266, which functions through worms 2I6 meshing with worm wheels 2I2. The rollers 266 are preferably urged toward the work by means of an actuator 2I4 (Figure 7) which connects with a rack bar 2I6. This rack bar 2I6 meshes with an intermediate gear 2I6, which, in turn, meshes with a rack bar 226. The rack bar 2I6 is coupled with the support which carries one of the rollers, and the rack bar 226 is coupled with the support which carries the other roller. Inthis manner the rollers are continually urged into frictional engagement with the work. Obviously other forms of actuator devices for maintaining frictional contact may be employed, as well as other driving means for rotating the rollers, without departing from the spirit and scope of the present invention. The actuation of the motor 266 may be controlled so as to arrest the movement. of the rollers when the work piece reaches the desired position within the machine. it will sufllce for the present inmounted within said housing. These thrust bearings I62 are positioned on opposite sides of a worm I64 or similar device which meshes with a vention to state that any suitable conventional control device for governing the degree of travel of the work piece may be employed. Forward work support The mechanism 52 (Figures 1 and 12) includes an upright base or frame 222, which at its upper end carries a pair of slidable clamping members 224 and 226. These clamping members are urged toward each other through the agency of a suitable power mechanism or motor 226, which acts through a screw 236. Obviously various forms of clamping devices may be employed for securing the projecting extremity of the work in place.

"As previously stated, the work is very heavy and hence, after a part has been cut oil, such part must be held in position so as to prevent it from v falling and possibly injuring the operator or the machine. The device operates on the principle of a vise, and, in view of the heavy work carried thereby, it is frequently necessary to employ power means for urging the clamping members 224 and 226 together. Obviously the invention is not in any sense limited to any particular type of power mechanism, and contemplates hydraulic or pneumatic control in instances Where such control is desired. It will also be noted that the support or clamping device 52 allows the work to be machined when they are not long enough to be clamped in the main clamping arrangement within the machine. It also permits the work to be machined at both ends without the necessity of turning the part around.

Safety device Particular attention is directed to Figure 3 wherein a pump 232 is driven from any suitable source. This pump draws fluid from a reservoir 234 provided within the frame 32 (Figure 1) through a conduit 236. This fluid is directed through a conduit 238 into a valve mechanism This valve mechanism includes a housing or casing 242 and a reciprocable valve member 244 within said housing, which is adapted when sufficient fluid pressure has been established within the conduit 236 to shift upwardly against a coiled spring 246. The upper end of the valve member 244 is connected with a valve stem 248, which, when moved upwardly, actuates a switch mechanism 256. When the valve stem 248 occupies its upper position, the switch mechanism 256 is conditioned to electrically connect the motor 46 with the source of power supply. However, when the fluid-within the conduit 236 falls, the valve 44 lowers and the switch mechanism automatically operates to cut out the motor 46. A conduit 252 connects with various points which are to be lubricated, for example, with passages 254 and 256 (Figure 1). which connect with the gear train driven from the motor 46 and alsowith a conduit 256 (Figures 1 and 5), which cornmunicates with the anti-friction bearing structure I26. It is of the utmost importance that these parts be continuously supplied with a lubricant, and should the pump 232 cease to supply the necessary lubricant pressure, the motor will automatically be cut out through the action of the switch mechanism 266. Obviously'various forms pf control mechanisms may be employed other than the specific arrangement disclosed herein. The switch mechanism 256 is commonly referred to in the, trade as a pressure switch. It will suflice to say-that the control mechanism must function to automatically cut out the motor when the lubricant pressure falls, and must also elec- Hydraulic control mechanism As previously stated, the valve mechanism I88 serves to control the speed and direction of movement of the actuator pistons I84, which cause the radial shifting of the tool holding devices 44. Referring to the circuit diagram in Figure 15, it will be seen that two feed pumps 266 and 262 are employed and also a rapid traverse pump 264. The valve mechanism is so constructed as to enable the simultaneous use of both feed pumps 266 and 262 when a relatively rapid inward feeding movement of the tools is required, and is also adapted to render the pump 262 functionally inoperative, thereby causing the pump 266 to propel said tools at a slower feeding rate. The rapid traverse pump 264 is employed to propel said tools at a rapid rate. These pumps are driven from any suitable source-such as an electric motor 266 shown in Figure 1. The pumps are mounted upon a unitary frame 268, which houses a reservoir 216 shown diagrammatically in Figure 15. The valve mechanism I98 includes a'main valve 212 and a feed control valve member 214. When the valve member 212 occupies its central or neutral position as shown in Figure 15, and the valve member 214 is shifted to the left from the position shown in said figure, fluid from the rapid traverse pump 264 passes througha conduit 216 and circulates through a passage 211 provided within the valve member 212 and back through a conduit 218 through a restricted orifice 286 into the reservoir 216. erse pump merely circulates and does not serve to propel the actuator pistons I84 in either direction.

Assume now that the work piece has been properly positioned in the machine and that the motor 46 is" operating to impart rotation to the rotary cutting mechanism 84. By shifting a control handle 282 of the valve mechanism I38 (Figure 2) to the right, the valve member 212 is urged to the left (Figure 15). In this position fluid from the rapid traverse pump 264 is delivered to the left end of the actuator cylinders I36 through conduits 284 and 286. Fluid from the right end of said cylinders passes outwardly through conduits 288 and 296 back through the valve mechanism I38 and into the return conduit 218. At this point attention is directed to a dog supporting slide 292 (Figures 1 and 2), which moves with the actuator pistons I34. One end of this slide 292 is coupled with the annular members I26 by a bracket 294, as clearly shown in Figure 1. The tools 96 are now being urged at a rapid rate inwardly toward the work piece 48 and the dog supporting slide 292 is moved to the right (Figures l and 2). Eventually a dog 296 engages a finger 298, which causes the valve member 212 to be returned to neutral. With the valve member 212 in this position andthe feed control valve 214 in theposition indicated in Figure 15, fluid from both of the feed pumps 266 and 262 is directed into the left ends of the cylinders I36. This feeding action occurs as the tools 86 engage the periphery of the work. Thi fast feeding movement of the tool continues un I la dog 866 engages the finger 298 and causes the valve member 212 to be slightly urged to the right. The

slight movement of the valve member 212 to the right'c'auses the feed control valve member 214 the'left (Figure 15). In

In other words, the rapid travpump 262 to circulate at substantially no pressure, and the pump 266 then functions alone to propel the tools 86 inwardly at a slower feeding rate. As the cutting operation is completed,

another dog 862 engages the outer end of a valve member 368, which, when urged to the right, permits fiuid from a chamber 364 at the right end of the valve mechanism I88 to be released, thereby enabling the pressure of the normal balancing fluid within a chamber 866 to cause the valve member 212 to be suddenly shifted to the right. In this position fluid is delivered by the rapid traverse pump 264 in a reverse direction to the actuators 42. This causes the rapid or" outward return movement of the tools to take place. In-

asmuch as the specific construction of the valve mechanism I88 is not being claimed in thepresent application, but is being claimed in co-pending applications Serial No. 627,025 filed July 30, 1932 and Ser. No. 696,284 filed November 1, 1933, a

detailed description thereof is not essential to a clear understanding of the present invention. It will suillce to stay that the-valve mechanism I36 is constructed and arranged so as to efficiently control the starting and stopping of theactuators 42, and also to control the rapid movement thereof, as well as the fast and slow feed thereof in the manner described above.

It will also be apparent that as the tools reach the limit of their outward movement, a dog 368 on the slide 298 engages a finger 3I6, thereby causing the valve member 212 to be automatically returned to neutral. In this position the rapid traverse pump, as well as the pumps 266 and 262, circulate, without imparting movement to the actuators 42. In the present embodiment the pumps are disclosed as being driven from a separate motor 266, but obviously said pumps may be driven from a single prime mover in instances where such a construction is more suitable.

Holder for external chamfering tool -adapted for chamfering the work piece. This holder is designated generally by the numeral 440, and issimilar in many respects to the tool holder mechanism 44 previously described. The mechanism 44:; includes a slide 62a, which is propelled and mounted in the same manner as the slide 62 previously described. An auxiliary slide or block 1611 is mounted upon the slide 62a. and is adapted to be shifted for purposes of adjustment with respect to the slide 620. by means of an adjusting screw 3I2. The block 16a also ca'rries'a chamfering tool 860. adapted to be adjustably secured in position by means of clamping members'88a and an adjusting screw 94a. The main difference in structuralarrangement of the tool holder 44a and the holder 44 resides in the manner in'which the tool 66a is yleldably urged to the left (Figures -16 and 18) through the action of a heavy coiled spring 3I4. Furthermore, a roller follower 3I6 is employed, which is adapted to bear against the periphery of the work piece 48, as clearly indicated in Figure 16. It will be noted that the tool 86a is particularly designed for forming an ex- Iiernal chamfer 48a upon the work piece 48. A slide or block 96a corresponding with the block 96 previously described carries the tool proper and is slidably mounted within the block 16a. By having the roller 3I6 follow along the periphery of the tube, a uniform chamfer will be cut regard-- less of the fact that the tube may not be rotating 0!; its true center. In other words,.ii' the tube is the result. However, when the tools 860 follow along the circumference of the tube by reason of the presence of the roller 3l6, the chamfer cut will be uniform with respect to the tube periphery.

Holder for internal chamfering tool which the tool 86?) is directly mounted, is pivoted at M8. Suitable. clamping means 88b is employed to secure the tool 86b within the pivoted block 90b. The inner or free end of the block 9017 carries a follower member 320, which is adapted to move within a slot 322 provided in a bracket 324. This bracket may be adjustably secured in a fixed position upon the member 80 by means of suitable ciamping bolts 326. It will be noted that the slot 322 includes a straight portion and a slightly curved portion. Thus, as the slide '62 begins its initial inward movement, no lateral movement is transmitted to the tool 8611. As the follower member 320 reaches the curved portion of the slot 322, the inner end of the tool 88 will be positioned so as to perform an internal chamfering operation when said tool is urged toward the inner circumferential corner of the work, this comer -being designated by the letter A in Figure 19. Movement of the follower member 320 within the curved portion of the slot causes the chamfering tool 866 to be shifted toward the corner A so as to perform the required internal chamfering action.

Summary From the foregoing it will be apparent that the present invention contemplates a machine tool whereby unusually heavy and bulky tubes may be cut oil, chamfered, and thelike in a very praccal manner. The described mechanism should be clearly differentiated from conventional cuttingofi machines wherein a rotary spindle is equipped with a chucklrigcollet for receiving the work. In such machines the work is rotated and a tool moves toward the work. These conventional machines are not adapted, to be used for performing the machining operations described herein. As previously pointed out, the weight and bulk of heavy tubing preclude the rotation thereof, unless a machine of tremendous size and strength is employed, the operation of which would require excessive power.- That is to say, the power required to operate such a device would be prohibitive in this day of highly developed methods of machine production. By employing the machine disclosed herein, the power for operating same is relatively small for the reason that the work is held stationary and the cutters are rotated. In the present machine, all of the stresses which would otherwise result from the centrifugal, bending or whipping forces occasioned during the rotation of an elongated work piece, such as atube, are completely eliminated The utilization of a plurality of cutters in the manner described herein, reduces the size of chip per tool, and at the same time causes the removal of a large amount of metal per unit of time. The hydraulic actuation of ,the cutting tools not only lends itself in this particular enand maintain is not properly centralized by the chuck and the roller SIS is not present, a non-uniform chamfer vlronment, but also presents a very desirable and safe feeding action which makes for increased rate of production. It will be apparent that the present invention contemplates a machine which is capable of machining very large, heavy tubes without the consumption of excessive power, and with a minimum amount of skill and effort on the part of an operator. While the machine is unusually rigid in design, it is not exceptionally large when one considers the heavy duty work it is called upon to perform. Furthermore, the complete automatic cycle of operation, coupled with the slow and fast feeding of the tools, materially contributes toward speed of production, as well as accuracy in the work performed.

The safety feature herein described, which causes the. driving motor to stop in the event of a decrease in lubricant pressure, presents a decided advancement in the art of machine tool design.

While certain hydraulic control features have been disclosed in this application, it should be understood that these control features per se, including the circuit arrangement and elements thereof such as control valves, pumps, and the like, do not form the subject matter of the present invention. The invention only contemplates such features when used in combination with the other structural arrangements disclosed herein.

While certain specific embodiments of the inverition have been disclosed herein, it should be apparent that modifications and changes in structural design may be made without departing from the spirit and scope of the appended claims. Having thus described the invention, what is claimed as new and desired to secure by Letters Patent is:

1. In a machine tool structure, a hollow rotary securing a work piece within the confines of said hollow carrier in a fixed position to be acted upon by tools on said carrier, tool holding means slidably mounted on said carrier and adapted to reciprocate toward and away from a supported work piece, and means for causing said tool holding means to experience variable speed and for causing the positive reciprocation thereof.

2. In a machine tool structure, a-hollow rotary tool carrier, a work support extending therein for securing a work piece within the confines of said hollow carrier in a fixed position to be acted upon by tools on said carrier, tool holding means slidably mounted on said carrier and adapted to reciprocate toward and away from a supported work piece, and means for causing said tool holding means to experience a rapid approach movement'and a slower movement during the operative functioning of the tool carried thereby.

3. In a machine tool structure, a hollow rotary tool carrier, a work support extending therein for securing a work piece within the confines of said hollow carrier in a fixed position to be acted i said carrier, tool holding means slidably mounted on said carrier and adapted to reciprocate toward and away from a supported work piece, and hydraulic actuator means for causing said tool holding means to experience variable speed during the v reciprocation thereof.

5. In a machine tool structure, a hollow rotary tool carrier, a work support for securing a work ciprocable on said carrier toward and away from the axis thereof, hydraulic actuator means for causing the reciprocation of said slides, and valve means for governing the degree of movement of all) said slides.

6. In a machine tool structure, a hollow rotary tool carrier, a work support extending therein adapted to secure a work piece in a fixed position within said hollow tool carrier, clamping means forsecuring said work piece on said support, tool holding means reciprocable on said carrier toward and away from a work piece supported therein, and actuating means including mechanism for causing said tool holding means to reciprocate in accordance with a predetermined speed of operation.

7. In a machine tool structure, a rotary tool carrier, a work support for receiving a tube or pipe to be machined, tool holding means slidably mounted on said carrier and adapted to reciprocate toward and away from a supported work piece, clamping means for securing the work piece on the support in position to permit said tool holding means to revolve around said work piece,

and power means for automatically causing said toolholding means to reciprocate in a direction toward and away from the center of a supported work piece or pipe and at various speeds, whereby to sever a selected length from said pipe.

8. In a machine tool structure, a hollow rotary tool carrier, an adjustable work support extending therein for securing a work piece within the confines of said hollow carrier in a fixed position to be acted upon by ,tools on said carrier, tool holding means slidably'rnounted on said carrier and adapted to reciprocate toward and away from a supported work piece, and means for causing said tool holding means to experience variable speed during the reciprocation thereof.

9. In a machine tool structure, a hollow rotary tool carrier, an adjustable work support extending therein for securing a work piece within the confines of said hollow carrier in a fixed position to be acted upon by tools on said carrier, tool holding means slidably mounted on said carrier andadapted to reciprocate toward and away from a supported work piece, means for causing said tool holding means to experience variable speed during the reciprocation thereof, and means for clamping the work in a fixed position upon the support.

10. In a machine tool structure, .a'rotary tool carrier, at work support positioned centrally with slidably mounted on said carrier and adapted to reciprocate toward and away from a supported work piece, means forcausing said tool holding means to experience variable speed during the reciprocation thereof, and means for advancing the work piece into position upon said work support.

12. In a machine tool structure, a rotary tool carrier, a work support for securing a work piece in position to be acted up0n by tools on said carrier, tool holding means slidably mounted on said carrier and adapted to reciprocate toward and away from 'a supported work piece, means for causing said tool holding means to reciprocate in a manner to effect the severing of awork piece, and fneans for receiving the severed sectionof said work piece and for gripping said work piece during the cutting operation.

13. In a machine tool structure, a rotary tool carrier, at work support extending therein for securing a work piece in a fixed position to be acted upon by a tool on said carrier, tool holding means slidably mounted on said carrier and adapted to reciprocate toward and away from a supported work piece, means for reciprocating said tool holding means, and power operated mechanism for advancing a work pieceinto position upon said work support.

14. In a machine tool structure, a hollow rotary tool carrier, a plurality of tool holding means slidably mounted upon said carrier and adapted to reciprocate toward and away from the axis thereof, work supporting means for receiving a work part or tube to be machined, said support being positioned within the'hollow tool carrier and including clamping means adjacent said tool holding means for securely holding the work against rotation, power actuated means for shifting the work part into a predetermined position for machining, and means for receiving and holding a severed section of said work part.

15. In a machine tool structure, a rotary too carrier, a work support for securing a work piece in a fixed position to be acted upon by a tool on said carrier, tool holding means slidably mounted on said carrier and adapted to reciprocate toward and away from a supported work piece, chamfe-ring and cut-oil means mounted in said work holding means, and means for causing the reciprocation of'said tool holding means.

16. In a machine tool structure, a rotary tool carrier, a work support for securing a work piece in a fixed position to be acted upon by a tool on said carrier, tool holding means slidably mounted on said carrier and adapted to reciprocate toward and away from a supported work piece, a tool mounted in said holding means for cutting an internal chamfer in the supported work piece, and means for causing the reciprocation of said work holding means.

1'7. In a machine tool structure, a rotary tool carrier, a work support for securing a work piece in a fixed position to be acted upon by a tool on said carrier, tool holdingmea'ns slidably mounted on said carrier and adapted to reciprocate to ward and away from 'a supported work piece, said tool holding means including a main slide and a tool holding member pivotally mounted thereon,

a chamfering tool carried by said pivoted member, and means for reciprocating said tool holding meansi 18.11'1 a machine tool structure, a] rotary tool carrier, 2. work support for securing a work piece in a fixed position to be acted'upon by a tool on sald carrier, tool holding means slidably mounted on said carrier and adapted to reciprocate toward and away from a supported work piece, said tool holding means including a main slide and a tool holding member shiftable upon said slide, a chamfering tool mounted in said shiftable member, means for controlling. the shifting of the member with respect to the slide to properly direct the tool in cutting a chamfer in the work pieee, and means for reciprocating said tool hold-- ing means.

19. In a machine tool structure, a rotary tool carrier, a work support for securing a work piece in position to be acted upon by a tool on said carrier, tool holding means slidably mounted 'on said carrier and adapted to reciprocate. toward and away from a supported work piece, power mechanism for imparting rotation to the tool carrier, means for supplying a lubricant to the moving parts in said carrier, and means for preventing the transmission of power to said carrier when the lubricant is not being properly supplied to the moving parts thereof.

20. In a machine tool structure, a main frame, a hollow rotary tool carrier mountedwithin said frame, a work support for securing a tubular work piece centrally with respect to and within said tool carrier, a plurality of tool holding means radially slidable upon said carrier toward and away from a supported work piece, means for securing said work piece against rotation, hydraulic actuator means coupled with said tool holding means and adapted to effect the simultaneous reciprocation thereof during the rotation of the carrier, and control mechanism for governing the speed and direction of movement of said hydraulic actuators in accordance with a predetermined cycleof movement of the tool holding means whereby, during the initial. movement of said tool holding means, a relatively fast travel is experienced toward the work piece, followed by a slower movement when the work is reached, and subsequently followed by a rapid reverse movement uponthe completion of the cutting operation, said cycle of operation being fully automatic.

21. In a machine tool structure, a hollow rotary tool carrier, a work support extending therein forsecuring a work piece within the confines of said hollow carrier in a fixed position to be acted upon by tools on said carrier, tool" holding means slidably mounted on said carrier and adapted to reciprocate toward and away from a supported work piece, and means for causing said tool holding means to be progressively fed into a supported work piece whereby to maintain uniformity in the distribution of load on said work piece and for positively moving said tool holding means awayfrom said workpiece.

-22. In a system of control for machine tools and the like, a work support, a tool support, means bricant pressure for controlling the operative functioning of said driving means.

23. In a system of control for machine tools and the 1ike, a work support, a tool support, means for imparting relative movement between said supports, one of said supports being rotatable, driving means for said rotatable support, means for supplying lubricant to the aforementioned parts, and means responsive to a decrease in lubricant pressure for controlling the operative functioning ofsaid driving means. I

24. In a system of control for machine tools and the like, a work support, a tool support, means for imparting relative movement between said supports, one of 'said supports being rotatable, driving means for said rotatable support, means for supplying lubricant to the aforementioned parts, and means operable when the lubricant pressure drops to apredetermined point to render the driving means functionally inoperative.

25. In a system of control for machine tools and the like, a work support, a tool support, means for imparting relative movement between said supports, one of said supports being rotatable, driving means for said rotatable support, separately driven means for supplying lubricant to one of aforementioned parts, and means responsive to variations in lubricant pressure for controlling the ioperative functioning of. said drivmg means. i

26. In a system of control for machine tools and the like, a housing, a tool spindle rotatably mounted therein, a prime mover for eflecting the rotation of the spindle, a lubricant circulating system for supplying lubricant to one of said aforementioned parts, and a switch operable by the lubricant circulating system for completing and maintaining the electrical circuit and eclecting the rotation of the spindle prime mover.

27. In a system of control for machine tools and the like, a housing, .bearings supported by said housing, a tool spindle rotatably mounted in said bearings, a lubricant circulating system including a prime mover for supplying lubricant to one of said aforementioned parts, a second prime mover for eflecting the rotation of the spindle, an electrical circuit for maintaining the operation of. the spindle prime mover, an electrical circuit for the lubrication circulating system prime mover, and -means connecting said prime mover circuits whereby the completion of the lubricant circulating system prime mover circuit eifects the completion of the spindle prime mover electrical circuit. x

28. In a machine tool, a housing, bearings supported by said housing, a tool spindle rotatably mounted in said bearings, a reservoir to supply oil, a pump to pump said oil; piping connecting the pump. to the bearings, a prime mover connectedto drive the pump, a separate prime mover constituting an electric motor connected to drive the tool spindle, an automatic pressure switch controlling the operation of the motor energizing the motor when it is closed and cutting out the motor. when it is opened, a pressure responsive mechanism in series in the piping so that oil must flow in the piping before it can move and conversely, it must move before it is flowing in the piping, and a mechanical connection between the pressure responsive mechanismand the pressure switch to close the switch when oil is flowing and open it when the oil stops flowing, whereby to insure a proper supply of oil to the bearings both when the spindle starts and while it is running.

PAUL R. GUIRL.

W. F. 8: JOHN BARNES COMPANY,

Assignce; By WM. W. BARTON,

- President.

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