US1501218A - Pipe-threading machine - Google Patents

Description

PIPE THREADING MACHINE Filed N 25. L921 12 Sheets-Sheet wmmllmll mu lllllllIllillllill"Ml|llllllllllllllliilllllll Mull] 1 ml mm ,4 I Q i i7 1 E if E v y g 1, v 1 M Wmgumw unnu- INVENTOR Jomv Jmmwoa/mc/ ATTORNEY V I J. 5. lMLACH inns 'rnamnme MACHINE I i e o 25. 1921 12 sheets-Shea INVEINTOR MVJIZ'VDKZGVMACH ATTORNEY July 15 1924. 1,501,218

J. 5. IMLACH PIPE THREADING momma r Filed New 25. 1921 12 sheets-sheet a INVENTOR tlamvmmzvmal.

ATTORNEY OJuly y 1,501,218 J. IMLACH [PIPE THREADING momma 8 F m 25 1921 12 Sheets-Sheet 4 immmmlmum mmmnmmmlll H wmmli 1 ATTORNEY July 15, 1924. 1,501,218

J. S. IMLACH PIPE THREADING MACHINE Fil d 25 1921 12 Sheets-Sheet 5 ATTORNEY July 15 1924. 1,501,218

J. S. IMLACH PIPE THREADING MACHINE I' f 8 B w P I .EE: 1 m N II I 3 .I M (I I:

I J k I! I g I I {Q Q l I F6 & I i 8 u I I g l I m 1 Q Q In H v {Q Ill E: Q u as II I I O m N R I I I g m a I la I?! lg! w p O r (I I] mvzmon JomvJmmwrozvhum ATTORNEY July 15, 1924. 1,501,218

J. 5. IMLACH PIPE THREADING MACHINE FlledNov. 25. 1921 12 Sheets-Sheet 8 g g I.

INVENTOR umv Wham,

' A'h'ORNEY July 15, 1924. 150L218 J. s. IMLACH PIPE THREADING MACHINE Filed Nov. 25 1921 12 Sheets-Sheet 9 l'wii l mvemon I71 (lo/11v Jmwz'zvsaivhucu.

ATTORNEY July 15 1924. 1,501,218

J. 5. lMLACH PI PE THREADI NG MACHI NE Filed Nov. 25, 1921 12 Sheets-Sheet 10 (ATTORNEY J. s. IMLACH PIPE THREADING MACHINE Filed Nov. 25, 1921 12 Sheets-Sheet ll :EI El]- INVENTOR Jonw Jrzmvsazvhucu.

A'TTORNEY 1,501,218 J. S. IMLACH PIPE THREADING MACHINE iled N 25, 1921 12 Sheets-Sheet 12 mvamon wrwo vmca ATTORNEY Til Patented July 15, 1924.

JOHN STEVENSON IMLACH, OF OTTAWA, ONTARIO, CANADA.

PIPE-THREADI N G MACHINE.

Application filed November 25, 1921.

T 0 all whom it may concern.

Be it known that I, JOHN STEVENSON IMLAGII, a citizen of the Dominion of Canada, residing at Ottawa, in the county of Carleton and Province of Ontario, Canada, have invented certain new and useful Improvements in Pipe-Threading Machines, of which the following is a specification.

The present invention comprehends the provision of a pipe threading machine and it is within the province of the disclosure to provide a machine of the character descri ed, embodying a circular milling cutter rotated and transversed by suitable means at proper ratio to produce a thread of the required lead.

Among other objects invention residing in the disclosure, are to provide indicators for the various speeds of the machine. said indicators graduated according to the nominal sizes of pipe for which the machine is adapted; to provide a circular milling cutter, the int'eed of which is controlled by a cam acting on a toggle connection to a false slide, the head carrying the said circular milling cutter to be con nected by adjustable means to the said false slide to accommodate for various sized pipe; to provide an indicator graduated according to the nominal sizes of pipe for the relative position of the circular milling cutter carrying head and false slide; to incorporate in a machine of the character described with the said indicator, a compensating dial graduated from the zero point and on both sides thereof so that adjustments may be made to compensate for variations in the sizes of the circular milling cutters used; to provide an indicator for the position of the cutting off tool, said indicator being graduated in accordance with the nominal sizes of pipe; to provide a burring tool for the removal of the burr from the inside of the pipe, said burr being caused by the cutting off tool in the cutting off operation; to incorporate in a machine of the character described, high and low ratio gearing introduced intermediate the point of the application of power and the spindle of the machine, either of which may be thrown in by a clutch to operate the machine atcutting off or threading speeds; to incorporate more than one cutter and necessary associated mechanism with a machine having but one spindle or pipe carrying means.

and aims of this Serial No. 517,635.

Many other objects will be readily perceived by a perusal of the disclosed matter, the invention residing in the novel features of construction and unique association of parts fully described and claimed, the descriptive matter being supplemented by the accompanying drawings, wherein:

Figure l is a side elevation of a machine constructed in accordance with my present invention.

Figure 2 is a top plan view of the machine as shown in Figure 1.

Figure 3 is an end elevation of the machine as shown in Figure 1.

Figure 4: is a side elevation of a duplex machine constructed in accordance with mv present invention.

Figure 5 is a top plan View of the machine as shown in Figure 4.

grammatically.

Figure 7 shows a longitudinal section of the opposite side of the gear box.

Figure 8 is a transverse vertical section as it would appear when taken on line 8-8 Figure 6 of the complete gear box mechanism.

Figure 9 is a transverse vertical section of the gear box as it would appear when taken on line 9-9 of Figure 6 of the complete gear box mechanism.

ing mechanism.

Figure 11 is a longitudinal section taken on line ll-l1 of Figure 10.

Figure 12 is a transverse vertical section taken on line 12-12 of Figure 10.

Figure 13 is a port ional bottom plan view of Figure 10.

Figure 14 is an elevation of mounted on the side of the venting motion of the cam shaft when high ratio spindle gearing is in motion.

Figure 15 is a longitudinal sectional ele vation taken on line 15-15 of Figure 14.

Figure 16 is a transverse'vertical section taken on line 16-46 of Figure 14.

Figure 17 is a similar view taken on line l7-17 of Figure 14:.

Figure 18 is a fragmentary plan view of the stop mechanism for preventing actuathe mechanism gear box for pre tion of the yoke employed for shifting the lead gears mounted on the cam shaft.

Figure 19 is a fragmentary sectional elevation illustrating the circular milling cutter head, false slide and the indicating mechanism working in conjunction therewith.

Figure 20 is a horizontal sectional elevation as it would appear when taken on line 20--20 of Figure 19.

Figure 21 is an end cular milling cutter dial.

Figure 22 is a sectional elevation illustrating the false slide which works in conjunction with the circular milling cutter head and the infeed cam and toggle mechanism.

Figure 23 shows in longitudinal section, the false slide and cutter head carriage with parts remaining in elevation.

Figure 24 is a fragmentary bottom plan view of the cutter elevation of the cirhead compensating head carriage illustrating more clearly the infeed and circular milling cutter head lead cams.

Referring to the drawings in detail. like characters of reference designate corresponding parts throughout the various drawings.

Referring now particularly to Figures 1, 2 and 3, the numeral 25 indicates the bed of the machine. The numeral 26 designates a spindle journalled in the bearings 27 and 28 and having mounted on the outer termi nals thereof, chucks 29 and 30 of conventional construction. The numeral 31 indicates the gear box cover. milling cutter head and 38 the cutting off tool head. The numeral 34 indicates the gear box on which the cover 31 is mounted.

Referring now particularly to Figures 6. 7, 8 and 9 which illustrate the gear box. the same will be preferably cast having bearings at the ends thereof. Journalled in the bearings 35 and 36 is the drive shaft 37. The numeral 38 indicates the intermediate feed shaft which is journalled in the bearings 39 and 4-0. The numeral 41 indicates the clutch shaft journalled in the hearings 42 and 43. 44 indicates the cluster gear shaft journalled in the bearings 45 and 46. The numeral 47 indicates the jack shaft journalled in the bearings 48 and 49, the hearing 49 being integral with. the bearing 39 for the intermediate feed shaft 38. The spindle drive shaft indicated by the numeral 50 is journalled in the bearings 51 and 53 indicates the sleeve journalled in been ings 54 and 55 and having the intermediate cam shaft drive shaft 56 partially enclosed in the same. The numeral 57 indicates the cam shaft which is journalled in the bean ings 58 and 59.

Referring now to the drive shaft 37. pulley 60 is mounted on one terminal thereof. This drive shaft 37 will be driven by a 32 the circular.

belt trained over the said pulley 60, which belt will be driven by a suitable source of motive power, such as an electric motor. Substantially mounted on the drive shaft 37 is the driving worm 61 and driving pinion 62.

Referring now to the intermediate feed shaft 38, the numeral 63 indicates the driving worm which is substantially mounted thereon and the numeral 6-1 indicates the worm wheel. The numeral 65 indicates the worm wheel which is mounted on the sleeve 66 which fits over the clutch shaft -11. This worm wheel 65 is driven by the driving worm 63. The numeral 67 indicates the double clutch mounted on the sleeve 66. 68 indicates the drive gear mounted on the sleeve 66 while the numerals 69 and 70 designate the first and second speed gears respectively. which are keyed to the shaft 41.

Referring now to the cluster gear shaft 44. the numeral 71 indicates the first speed gear and the numeral 72 the second speed gear. The numeral 73 indicates the first speed gear, 74 the second speed 75 the third speed gear. The gears 73, 74: and 75 are slidably mounted on the shaft 44 and are provided with key seats for engagement with the key 76. The numerals 77 and 7 8 indicate the shift gear collars for restricting the movement of the gears on the cluster gear shaft 44.

Referring now to the jack shaft 47, the numeral 79 designates the first driven gear.

80 the third driven gear and 81 the second driven gear. The numeral 82 indicates the first jack shaft driving gear and 83 the second jack shaft driving gear. The jack shaft driving gears 82 and 83 are slidably mounted on the jack shaft 47 and are provided with key seats for engagement with the key 84. The numeral 85 indicates a gear collar substantially mounted on the jack shaft 47 which is functioned to restrict the movement of the jack shaft driving gears 82 and 83. Referring now particularly to the spindle drive shaft 50, the numeral 86 indicates the first driven gear and 87 the second driven gear. The numeral 88 indicates the spindle drive pinion, while the numeral 89 indicates the cam shaft drive pinion which meshes with the cam drive gear 90 mounted on the sleeve 91 which is substantially secured to the intermediate cam shaft drive shaft 56. The numerals 92 and 93 designate lead pinions. while the numerals 94 and 95 indicate lead gears slidably mounted on the cam drive shaft 57 and provided with key seats for engagement with the key 96. The numeral 97 indicates a flange integral with the hub 180 of the lead gears 94 and 95.

Referring now particularly to Figure 2. the spindle drive pinion 88 illustrated in dotted lines. drives the spindle gear 98 also illustrated in dotted lines. This spindle gear and gear 98 is circumposed about and substantial with the spindle 26.

Referring now to Figures 2, 6 and 7, the numeral 99 indicates a drive pulley which is mounted on the shaft 37 at the opposite end to the drive pulley 60. The function of this drive pulley {)9 will be hereinafter explained.

The numeral 101 indicates an intermediate shaft coupling the drive shaft 37 and the shaft 105 journalled in the cutter head carriage.

Referring now particularly to Figure 20, the shaft 105, journalled in the cutter head, is provided with ball races 106 and 107 to facilitate the rotation of the same. This shaft is capable of reciprocating motion to compensate for the advancing and Withdrawing of the cutter head carriage. The numeral 108 indicates the drive pinion which is formed on the drive shaft 105. This drive pinion 108 drives the intermediate gear 109 mounted on the intermediate gear shaft 110 suitably journalled in the cutter head. The intermediate gear 109 drives the intermediate gear 11] mounted on the sleeve 112 having a pinion 113 formed on the same. Sleeve 112 is mounted on the compound drive shaft 114 which is suitably journalled in the cutter head. The pinion 113 drives the spindle gear 115, which is mounted on the spindle 116 in a suitable manner. On one terminal of the spindle 116 is mounted the circular milling cutter 117 which is secured in position by means of the nut 118. The plates 119 and 120 are positioned over the terminals of the shafts and spindle. From the foregoing, it will be readily perceived that the power transmitted from the main drive shaft 37 through the gearing as set forth, will drive the circular milling cutter for performing its operation.

The cam shaft 57 extends through one end of the gear box 34 as clearly illustrated in Figure 2. Referring now particularly to Figures 22, 23 and 24, the cam shaft 57 has engagement with the cutter head carriage 121 by passing through the bearings 122 and terminating in the adjusting hand wheel sleeve 123 which is substantially secured to the said cam shaft. The function of this adjusting hand wheel will be further explained hereinafter.

Mounted on the cam shaft 57 is the lead cam 124 which is provided with an annular groove 125 for engagement with the cam roll 126. The numeral 127 indicates the infeed cam, the configuration of which is more clearly illustrated in Figure 22. The numeral 128 indicates the cutter head or false slide, as it will be hereafter termed. The false slide 128 is dovetailed into the cutter head carriage as at 129 and the cutter head carriage is provided with a gib 130 to facilitate adjustment when necessary. The false slide 128 is provided with the dovetail slide 131 for engagement with the cutter head carriage 32. This dove-tail slide is also provided with a gib designated by the numeral 132. The infced cam 127 acts upon a toggle constituting the links 133 and 13+. Link 133 is pivotally connected on one ter minal by the slide link pin 135, while the link 134 is pivotally connected at its oppo site terminal to the fulcrum pin 136. The numeral 137 indicates a cam roll pin which connects the inner terminals of the links 133 and 134. Disposed intermediate the jaws of the link 134 is cam roll 138 which is rotatably mounted on the cam roll pin 137 and bears against the periphery of the infeed cam 127. From the foregoing, it will be apparent that the link pin 135 engages the toggle and the fulcrum pin 136 with the carriage 121. In operation, the cam roll 138 has contiguous engagement with the periphery of the infeed cam 127. This contiguous cugagement spring 139, one terminal of which is connected to the cam roll pin 137 and the cross feed spring bolt 140. clearly shown .in Figure 24. The cutter head carriage is mounted on the false slide 128. The false slide. 128 is provided with an integral bracket lll which is provided with a head 142 and an aperture therein designated by the numeral 143. Passing through the aperture 143 is a worm shaft 144 shown in Figure 19. which has engagement with the bushing 145 rigid with the cutter head carriage 32. On the outer terminal of this worm shaft 144 is mounted indicator mechanism as will be hereafter fully described.

Referring again to the gear box mechanism, the numeral 31 indicates the cover for the same. Mounted on this cover is the mechanism for shifting the gears into proper ratio for threading and cutting off speeds. I will first explain the action of the two-way clutch and its controlling mechanism, which constitutes a rectangular bar indicated by the numeral 146 which is slidably mounted in the brackets M7 and 148. Mounted on this rectangular bar is a yoke 149, the function of which will be hereinafter explained. This rectangular bar 146 is shifted by means of the lever arm shown in Figure 2 and indicated by the numeral 150. Lever arm 150 is mounted on the upper terminal of the vertical rod '15]. which has substantially secured thereto, a crank 152, the bifurcated terminal of which straddles the pin 153 which is mounted on the rectangular bar 146.

Referring now particularly to Figure 10, which shows the indicating mechanism. the indicator point 154 integral with the lever arm 150 is turned so that the same coinwith the false slide 128 is brought about by the coil cides with the graduation A. In this position. the clutch 67 is disengaged and the clutch shaft 41 is motionless. If it is desired to operate the machine at threading speed, the lever arm 150 is turned so that the indicating point 154 coincides with B. This will operate the machine in the proper speed for performing the threading operation. If it is now desired to shift the mechanism into cutting off speed, the lever arm 150 is moved in acontrary manner so that the indicator point 154 coincides with the graduation In this position, the clutch operates the mechanism for the cutting off speed. Referring again to Figures 10, 11, 12 and 13, on the top of the cover are mounted the gear shift lever arms 155, 156

and 157. On one terminal, the gear shift lever arm 155 is connected to the vertical pin 158 which extends through the cover 31 and has a crank 159 mounted on the lower terminal thereof. The bifurcated terminal of this crank straddles the pin 160 mounted on the gear shift yoke 161 which is slidably mounted on the longitudinal guide bar 162. The gear shift lever arm 156 is connected on one terminal to the pivot pin 163 which has a crank 164 mounted on the lower terminal thereof, congruent to the, crank 159. The bifurcated terminal of this crank straddles the pin 165 mounted on the gear shift yoke 166 which is also slidablv mounted on the longitudinal guide bar 162. D I

Referring now to the gear sh ft lever arm 157. one terminal of the same is connecte to the rod 167 which is of considerable length in relation to the pivot pins 158 and 163. Mounted on the lower terminal of this rod is the crank 168 which straddles the pin 169 mounted on the gear shift yoke 170 which is slidably mounted on the longitudinal guide bar 171. The opposite terminals of these gear shift lever arms 155, 156 and 157 slide in the recesses or guide channels 172 and 173. These gear shift lever arms are provided with suitable terminals for engagement with the apertures.

174 to prevent movement of the samewhen in the proper position. The construction o the heads ot these gear shift lever'arms is conventional and need not be explained in detail. These gear shift lever arms may be provided with locking. mechan sm, but in consideration of the construction of the same being in common use, it is thought unnecessary to give a detailed explanation of the same.

Referring now to Figures 6 and 7, 8 and 9. the gear shift yoke 161 straddles the first and second speed gears designated by the numerals 71 and 72 which are mounted on the cluster gear shaft 44. Yoke 166 straddles the first, second and third speed gears designated by the numerals 73, 74

and also mounted on the cluster gear shaft 44. Yoke 170 straddles the first and second driving gears designated by the numerals 82 and 83 mounted on the jack shaft 47. In operation, the first and second speed gears 71 and 72 are driven by the first and second speed gears 69 and 70. The first, second and third speed gears 73, 74 and 75 drive the first, second and third driven gears 79, and 81. The first and second driving gears 82 and 83 mounted on the jack shaft 47 drive the first and second driven gears 86 and 87 mounted on the spindle drive shaft 50.

In the accompanying drawings, I have illustrated the gears set for threading a three inch pipe. W'hen it is desired to thread a pipe of this size. the lever arm 150 is turned so that the indicator designated by the numeral 154 coincides with the graduation B. Power is transmitted from the drive shaft 37 through the driving worm 61 to the intermediate feed shaft 38 hv means of the Worm wheel 64. The driving worm 63 drives the worm wheel 65 and power is transmitted through this medium to the clutch shaft 41. The first speed gear 76 now drives the second speed gear 71, thus rotating the cluster gear shaft 44 at the proper speeed. The third speed gear designated by the numeral 75 drives the first driven gear designated by the numeral 79 on the jack shaft 47. The first driving gear 82 drives the first driven gear 86. The cam drive pinion S9 drives the cam drive gear 90, which is mounted on the intermediate cam shaft drive shaft 56. The lead gears 94 and are now shifted so that the lead gear 95 meshes with the lead pinion 93. This drives the cam shaft at the proper ratio for the driving of the circular milling cutter designated by the numeral 117, see Figure L0. The shifting of the lead gears 94 and 95 will be explained hereafter.

\Vhen it is desired to cut the pipe, the indicator 154 integral with the lever arm 150 coincides with the graduation C. Power is then transmitted from the drive shaft 37 through the drive pinion 62 and the drive gear 68. The gearing in this manner drives the spindle at a high speed required for the cutting operation. It will be appreciated that the gearing hereinbefore described, is constructed to operate the machine at various speeds for performing operations on various nominal sized pipes. It is thought, however, that a detailed description for each gear shaft is unnecessary as the mode of operation is similar to the one hereinbefore described.

Referring to the lead shift gears 94 and 95, the same are illustrated in neutral position. \Vhen it is desired to shift the same to operate the cam shaft 57, the yoke 175 mounted on the slide bar 176 is operated by the shoulder 189 formed on the cam shaft 57 is actuated.

by the crank 177 which is in turn operated by the shaft 178 extending through the body of the machine and actuated by the vertical lever arm indicated by the numeral 179. This yoke 175 straddles the lead gears 9e and 95 and moves the same to the right or the left in accordance with the movement of the lever arm 179. These lead gears 94 and 95 are mounted on the hub 180 which is provided with the integral flange 97 on the outer terminal thereof, which flange is provided with a slot 181 to clear the control trip 182 shown in Figure 14 when the gears are thrown into operating position. hen the same start to revolve, the slot in the gear hub indicated by the numeral 181 is carried past the control trip trip bears on the side of the flange and holds the gears in mesh until such time as this slot in the flange is again opposite the control trip, at which point the gears return to neutral position, having completed one revolution. The return of these gears to the neutral position is obtained by the coil springs 183 and 184 bearing against the washers 185 and 186, which bear against the extended bifurcated terminal 187 of the crank 177 and are free to move on the release guide 188, but limited in their travel guide, Which shoulder is straddled by the bifurrated terminal 187 of the crank 177. The vertical shaft ll'ilextending from the clutch operating shaft carries at its lower terminal a collar 190 which collar is provided with a segmental recess 191 to clear the pin 192. This pin is bevelled on its inner terminal as at 193, shown in dotted lines to enter the shallow aperture 194 in the shift bar 176. This pin 192 is held in position by the coil spring 195. Then the clutch is in neutral position or slow speed, the segmental recess 191 formed in the collar 190. is opposite the outer terminal of the pin so that the yoke 175 mounted on the shift bar 176 may be moved end ways to shift the gears. When the clutch is in high speed, the segmental recess 191 is not in line with the pin 192 so that this pin cannot move end ways and come out of engagement with the aperture 194 formed in the shift bar 176 and thus locks this yoke in a neutral position. lVhen either the lead gear 94 or the lead gear 95 is engaged the pin 192 projccts into the segmental recess 191 which is of such length as will permit the clutch lever 150 to be shifted freely between neutral and slow speed positions, but if it is attempted to engage the clutch in high speed position the end of the segmental recess 191 strikes the pin 192 and prevents motion of the clut h shifted in this direction. When either of the lead gears is in mesh with either of the lead gear pinions, the The actuation of 182 so that the. T

this cam shaft causes the lead and advance cams 127 and 121 respectively to operate, thus causing the infecd and advance of the circular milling cutter 117.

Referring again to Figures 2, 3 and 4, the numeral 32 indicates the cutter head having mounted thereon a cutter 196. The numeral 197 indicates a burring tool mounted on the arm 198 slidably mounted in and supported by the cutter head 32. The infeed of the cutter is controlled by the hand wheel 199. The numeral 200'indicates the indicator for the relative position of the cutter head carriage, which advances or withdraws the carriage to compensate for variations in the nominal sizes of pipe. he construction of this cutter head carriage, cutting and burring tool mechanism is of conventional construction and, therefore, it is thought unnecessary to give a detailed explanation of the same.

Referring now to the lul'iricati'ng means, the numeral 201 indicates the force feed pump driven by the belt 202 trained over the drive pulley 99 and The lubricant is contained in a suitable reservoir in the base of the machine and the same is conducted through the main lead pipe 204 and the sublead pipes 205 and 206 to lubricate the circular milling cutter and the cutting off and burring tools.

In operation, the pipe to be milled, cut or burred is positioned in the spindle 26 and secured in the chucks 29 and 30. If the pipe to be milled, cut or burred is seven inches in diameter, the gear shift lever arms 156, 157 and 158 are shifted to coincide -with the graduations on the gear box indicating that nominal sized pipe.

The cutting off operation is first performed. The controlling lever arm 150 is turned until the indicator 154 coincides with the graduation (l, resulting in power being transmitted through the high ratio gearing as hereinbefore described, to perform the cutting operation. In this case, pinion 62 drives the gear 68 and the gears and 71, and 79, 83 and 87 will be in mesh. The indicator 200 is then adjusted for seven inch pipe and the cutting operation is performed by advancing the cutter head carriage 32 through the medium of the hand wheel 199. After the cutting oporation. the burr is removed from the inner end of the pipe caused by the cutting operation. This burr is removed by the burrin tool 197 mounted on the adjustable holder 198.

After the burring operation, the indicatin dial 207 is turned until the graduation for the seven inch pipe coincides with the terminal of the indicator 208. This operation seats the cutter head carriage to perform its operation on a pipe of that size. The controlling lever arm 150 then turned the pulley 203.

until the indicator 154 coincides with the graduation B, resulting in power being transmitted through the low ratio gearing as hereinbefore described. The lead gears 94 and 95 are then thrown in, the lead gear 95 being driven by the pinion 93. Simultaneously as these gears are thrown in, the cam shaft 5'? is caused to rotate and the lead cam 1% follows the stationary cam roll 126, advancing the cutter head carriage and cynchronically, the infeed cam 127, acting oil the cam roll 138 of the toggle connection, causes the infeed of the cutter head carriage through the medium of the false slide connection. When the lead gear 195 is thrown into mesh, the cam roll 138 will be positioned on that undulated portion of the cam indicated'by the numeral 209. The gradual infeed of the cutter is accelerated to its full cutting depth by the curvature of the periphery of the cam and when the same has reached a certain point, the cam roll 186 follows the concentric face of the cam until the full thread is cut. The cam roll 138 then meets with the undulation 209 and the spring 139, acting on the toggle connection, causes the false slide to withdraw. Upon the completion of the milling operation, the slot 181 coincides with the controlling trip 182 and the coil spring 188 throws the gears out of mesh. It will be perceived that this completes the operation on the pipe.

After the circular milling cutter 117 is used for a period of time, the same be comes dull and it is required to grind the same. diameter and therefore, it is necessary to adjust the cutter head carriage to compensate for this variation. If the diameter of the circular milling cutter has been reduced, say .0005 of an inch, the dial 210 illustrated in Figures 1.9 and 21 is turned so that the zero point on the vertical face of the indicator 207 coincides with that respective number of graduations indicated thereon. This operation will advance the cutter head carriage 32 to compensate for this variation in the diameter of the cutter.

It is often found necessary to rethread threaded pipes and therefore, it is necessary to adjust the cutter head carriage so that the teeth on the circular milling cutter will properly coincide with the threads on the pipe to be rethreaded. So that the cutter head carriage may be readily adjusted, I have threadedly engaged the ad justable handle wheel sleeve 123 with the cutter head carriage as at 211. It will be readily perceived that by turning this adjustable hand Wheel sleeve. the cutter head carriage will be advanced :or withdrawn so that the, teeth on the circular milling cutter will properly coincide with the This grinding operation reduces the threads on the pipe to be rethreaded. The adjustable hand wheel sleeve is held in adjusted position by means of the bolt 212 passing through the collar 213.

In Figures 1 and 5, I have illustrated a duplex machine embodying but one rotary spindle and pipe holding means. The gear box mechanism is inbefore described. On both terminals of the machine, I have provided threading, cut off and burring mechanism which will operate in a congruent manner to that of the previously described machine. This machine is especially adapted for pipes of considerable weight and length as it will be readily understood that it is unnecessary to remove the pipe from the machine and turn the same end to end, as the same may be carried through the spindle of the machine and the threading; cutting off and burring operations performed on the oppo' site end thereof.

From the foregoing description, it is thought that the advantages, construction and operation of my invention will be readily apparent and while I have illustrated similar to that hereand described the preferred construction of my invention, I desire to have it understood that the deviations from such details in the adaptation of the machine for commercial purposes may be resorted to as do not form a departure from the spirit of the invention as defined by the appended claims.

\Vhat I claim as new is:

1. A pipe threading machine consisting of a frame, a pipe holding spindle supported and rotatably geared in said frame, a head reciprocally supported on said frame, a circular milling cutter rotatably mounted on said head, a cutting off tool frame mounted for movement longitudinally and transversely of said first-named frame, and a means of rotating said pipe holding spindle and said circular milling cutter.

2. A pipe threading machine consisting of a frame,- a pipe holding spindle supported and rotatably geared in said frame, a head reciprocally supported to move longitudinally of said frame, a portion of said head reciprocally supported to move transversely of said frame,' a cutting off tool frame mounted for movement longitudinally and transversely of said first-named frame, a circular milling cutter rotatably mounted on said head and a means of rotating said pipe holding spindle and said circular milling cutter.

3. A pipe threading machine consistin of a frame, a pipe holding spindle supporte and rotatably geared in said frame, a head reciprocally supported to move longitudinally of said frame, a portion of said head reciprocally supported to move transeversely of said frame. a cutting off tool frame mounted for movement longitudinally and transversely of said first-named frame, a circular milling cutter rotatably mounted on said head, a means of rotating said pipe holding spindle and said circular milling cutter and an indicator carried by said head to indicate the relative position at which said circular milling cutter should be positioned when cutting different nominal sizes of pipe.

4. A pipe threading machine consisting of a frame, a pipe holding spindle supported and rotatably geared in said frame, a head reciprocally supported to move longitudinally of said frame, a portion .of said head reciprocally supported to move transversely of said frame, a cutting off tool frame mounted for movement longitudinally and transversely of said first-named frame, a circular milling cutter rotatably mounted on said head, a means of rotating said pipe holding spindle and said circular milling cutter, an indicator carried by said head to indicate the relative position at which said circular milling cutter should be positioned when cutting different nominal sizes of pipe and indication marks formed on said indicator corresponding to the nominal sizes of pipe.

5. A pipe threading machine consisting of a frame, a pipe holding spindle sup ported and rotatably geared in said frame, a head reciprocally supported to move longitudinally of said frame, a portion of said head reciprocally supported to move transversely of said frame, a cutting off tool frame mounted for movement longitudinally and transversely of said first-named frame, a circular milling cutter rotatably mounted on said head, a means of rotating said pipe holding spindle and said circular milling cutter, an indicator carried by said head to indicate the relative position at which said circular milling cutter should be positioned when cutting different nominal sizes of pipe, indication marks formed on said indicator corresponding to the nominal sizes of pipe and means whereby a portion. of said indicator may be movable and adapted to be adjusted to accommodate variations in the diameter of said cutter.

6. A pipe threading machine consisting of a frame, a pipe holding spindle supported and rotatably geared in said frame. a head reciprocally supported to move longitudinally of said frame, a circular milling cutter rotatably mounted on said head, a means of rotating said pipe holding spindle and said circular milling cutter, a cam controlling the longitudinal reciprocal motion of said head.

7. A pipe threading machine consisting of a frame, a pipe holding spindle supported and rotatably geared in said frame, a head reciprocally supported to move longitudinally of said frame, a means of rotating said pipe holding spindle and said circular milling cutter, a cam controlling the reciprocal motion of said head, the ratio of rotation between said cam and said spindle being such that said spindle Will make more than one revolution to one of said cam, thus giving the said circular milling cutter the necessary time to advance to the depth of the thread and make one complete revolution of the pipe While at full depth and then withdraw.

8. A pipe threading machine consisting of a frame, a pipe holding spindle supported and rotatably geared in said frame, a head reciprocally supported to move longitudinally of said frame, a portion of said head reciprocally supported to move transversely of said frame, a cam, a toggle mechanism carried by said portion to operate in conjunction with said cam to cause the transverse reciprocal motion to said portion at predetermined intervals, a circular milling cutter rotatably mounted on said head, a means of rotating said pipe holding spindle, said circular mi ling cutter and said cam.

9. A pipe threading machine consisting of a frame, a pipe holding spindle supported and rotatably geared in said frame, a head reciprocally supported to move longitudinally of said frame, a portion of said head reciprocally supported to move transversely of said frame, a circular milling cutter rotatably mounted on said head, a means of rotating said pipe holding spindle and said circular milling cutter, a cutting off tool frame reciprocally supported to move longitudinally and transversely of said frame and a cutting off tool carried by said cutting off tool frame adapted for cutting off lengths of pipe held by said pipe holding spindle.

10. A pipe threading machine consisting of a frame, a pipe holding spindle supported and rotatably geared in said frame, a head reciprocally supported to move longitudinally of said frame, a portion of said head reciprocally supported to move transversely of said frame, a circular milling cutter rotatably mounted on said head, a means of rotating said pipe holding spindle and said tool frame reciprocally supported to move longitudinally of said frame and transvers cutting off lengths of pipe held by said pipe holding spindle and a graduated indicator thereon referring to the different nominal sizes of pipe whereby said cutting off tool frame may be properly adjusted in relation to the position of said circular milling cute ter.

11. A pipe threading machine consisting of a frame, a pipe holding spindle supported and rotatably geared in said frame, a head reciprocally supported to move loncircular milling cutter, a cutting off lji) ' of rotating said pipe ting off ed and rotatably geared gitudinally of said frame, a portion of said head reciprocally supported to move transversely of said frame, a circular milling cutter rotatab-ly mounted on said head. a means holding spindle and said circular milling cutter, a cutting off tool frame reciprocally supported to move longitudinally and transversely of said frame, a cutting off tool carried by said cuttool frame adapted for cutting off lengths of pipe held by said pipe holding s indle and a burr cutting member carried by said cutting off tool frame.

12. A pipe threading machine consisting of a frame, a pipe holding spindle support ed and rotatably geared in said frame, a head reciprocally supported to move longitudinally of said frame, a portion of said head reciprocally supported to move transversely of said frame, a circular milling cutter rotatably mounted on said head, a means of rotating said pipe holding spindle and Said circular milling cutter, a cutting off tool frame reciprocally supported to move longitudinally and transversely of said frame, a cutting off tool carried by said cutting off tool frame adapted for cutting off lengths of pipe held by said pipe holdin spindle and a burr cutting member carrie by said cutting off tool frame, said burr cutting member disposed angularly and reciprocally in last said frame.

13. A pipe threading machine consisting of a frame, a pipe holding spindle sup ported and rotatably geared in said frame, a head reciprocally supported to move longitudinally of said frame, a portion of said head reciprocally supported to move transversely of said frame. a circular milling cutter rotatably mounted on said head, a means of rotating said pipe holding spindle and said circular milling cutter, a cutting off tool frame reciprocally supported to move longitudinally of said frame and transversely of said frame, a cutting off tool carried by said cutting ofi tool frame mounted for longitudinal and transverse movement adapted for cutting off lengths of pipe held by said pipe holding spindle and a burring tool disposed angularly in the last-named frame and adapted for removing a burr from the said pipe.

14-. A pipe threading machine consisting of a frame, a pipe holding spindle supportin said frame, a circular milling cutter rotatably mounted and supported from said frame to be reciprocated thereon, a means of rotating said circular milling cutter, a cutting off tool reciprocally mounted on said frame mounted for longitudinal and transverse movement,

a means for rotating said pipe holding spindle at various predetermined rates of speed from a fixed speed drive shaft.

15. A pipe threading machine consisting of a frame, a pipe holding spindle support ed and rotatably geared on said frame, a circular milling cutter rotatably and reeip rocally supported on said frame, a means of rotating said circular milling cutter at a fixed rate of speed, a set of high and low ratio gearing introduced intermediate the point of application of power and the said pipe holding spindle, mechanism adapted to either the high or low ratio gearing, whereby a high speed on the said pipe holding spindle is obtained for cutting off and low speed on the said pipe holding spindle for threading. 7

v 16. A pipe threading machine consisting of a frame, a ipe holding spindle supported and rotata ly geared in said frame, a head reciprocally supported to move longitudinally of said frame, a portion of said head reciprocally supported to move transversely of said frame, a circular milling cutter rotatably mounted on said head, means of rotating said circular milling cutter at a fixed rate of speed, a set of high and low ratio gearing introduced intermediate the pointof application of power and the said pipe holding spindle, mechanism adapted to the high or low ratio gearing and a locking mechanism whereby said head cannot be reciprocated on the said frame when said high ratio gearing is in operation.

17. A pipe threading machine consisting of a frame, a pipe holding spindle supported and rotatably geared in said frame, a head reciprocally supported to move longitudinally of said frame, a portion of said head reciprocally supported to move transversely of said frame, a circular milling cutter rotatably mounted on said head, means of rotating said circular milling cutter at a fixed rate of speed, a set of high and low ratio gearing introduced intermediate the point of application of power and the said pipe holding spindle, mechanism adapted to the high or low ratio gearing and a locking mechanism whereby said high ratio gearing cannot be put into operation while said head is reciprocally moved into operative threading position.

18. A pipe threading machine consisting of a frame, a pipe holding spindle supported and rotatably geared in said frame, a circular milling cutter rotatably and reciprocally supported on said frame, a means of rotating said circular milling cutter at a fixed rate of speed, a set of gears suitably supported and operated in conjunction with last said means, gear movers for adjusting the relative position of said gears, handles operating said gear movers, indication marks in the path of movement of said handles so that said handles may be positioned at certain points to operate certain of said gears at a predetermined rate of speed, ac-

cording to the size of the pipe in said pipe

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