Universal Pipe Lathe

The necessity of providing a juncture on a pipe that is professionally finished so that it can be fastened to an adjoining pipe with a defect-free weld has been appreciated for some time. In pipe lines, nuclear reactors, and the like, the necessity to provide junctures that are reliable and durable are of the utmost importance. Frequently, the working conditions associated with pipe machining equipment have been quite hostile either to the machine or to the machine operator. For example, in nuclear reactors the necessity for pipe replacements has been such that these types of maintenance procedures are quite frequently occurring and maintenance personnel may only work in an area that is radioactively hot for extremely short periods of time. Accordingly, the desirability of an apparatus for finishing pipes which once set up can proceed automatically, and can be initialized in a minimum amount of time has found increasing importance and acceptance in industry.

Prior art devices which have attempted to address these problems in the past include the following U.S. Pat. Nos.:

2,769,234--Young

2,145,191--Pennington

3,644,977--Valentine

3,650,514--Stunkard

3,942,248--Sherer et al.

3,807,047--Sherer et al.

3,744,356--Slator et al.

3,875,831--Beauloye

4,050,335--Gilmore

3,762,246--Becker

3,772,944--Becker

These references while generally being directed to pipe working machinery, neither contemplate nor provide for the advantages associated with the mechanism according to the instant application.

Specifically, it is to be noted that the prior art provides for a drive mechanism in which a rotating ring is provided with a circumferential ring gear that is totally exposed and open to the elements. Clearly, when a machining operation is to occur, particulate matter such as shavings and other enviromental contaminants can interfere with the motor drive mechanism as it relates to the ring gear and can therefore provide binding in the rotation to the detriment of the work. Additionally however the exposed ring gear provides a needless hazard for the operators of the machinery, and such a hazard can be substantially magnified when working in close quarters, or in other difficult conditions such as underwater cutting and especially in combustible areas.

Additionally, the prior art fails to provide for the mechanism according to the present invention in that the indexing mechanisms are not provided on the same face of the rotating implement as the cutting tool. This, of course, makes the set-up operation for pipe working somewhat more laborious. In addition, while some of the prior art devices attempt to provide mechanism which can accommodate pipes that are not perfectly round, the actual centering operation of these mechanisms is somewhat more laborious than that which is taught in the instant application. The clamping devices according to the present invention cause this lathe to operate accurately on hollow or solid stock having square, circular, or any other external geometric configuration.

Furthermore the unique overall structure of the lathe according to the present invention does work which heretofore required two different machines: that is to say the mechanism according to the present invention has the versatility to serve as both a vertical turret lathe and an engine lathe.

Accordingly, this invention has as an objective to provide a universal pipe lathe which is capable of being affixed to the pipe in a relatively easy manner and also to assure that the pipe is symmetrically located relative to the lathe.

A further object contemplates providing an apparatus of the character described above which, when it encounters a pipe having a deformation, can easily reform the pipe back into an undeformed condition.

It is yet another object of this invention to provide a device of the character defined above which is reliable, durable in construction, and easy to operate.

It is a further object of this invention to provide a device of the character described above in which the cuts made on the pipe are of the highest quality, so that any associated and ensuing operation can be performed with a high degree of surety that welds and the like will not fail.

It is a further object of this invention to provide a device of the character described above which is capable of performing a diverse array of cutting operations, in which one cutting operation may proceed automatically and/or sequentially to the next with a minimum amount of down time.

These and other objectives are achieved by the apparatus of the present invention by providing a device which is separable along two areas of its ring structure so that it may be opened and allowed to straddle a continuous section of pipe, or alternatively may be suspended and supported by the internal portions of a pipe should only the end of the pipe be accessible. Furthermore, the mechanism to be described hereinafter provides a variety of suspension mechanisms for supporting the lathe prior to its installation on the pipe, for ease in its use. The mechanism to be described hereinafter provides a stationary ring upon which at least one drive motor is provided which drives a second rotating ring by a preferably beveled ring gear on a side face of the ring. On an opposed side face, plural diverse cutting tools are capable of being fastened thereon along with a unique indexing mechanism which allows the machine when set up to be operated automatically without further supervision. The various cutting tools allow diverse operations such as internal and external parting-off, internal and external beveling, plunging, ring cutting, and internal boring to be accomplished along various lengths of the the pipe automatically at variable angles or degrees. Pipe facing and de-burring are also equally accomplished, and the automative indexing system allows for the mechanism to provide incremental cutting at a maximum rate.

It is still a further object to provide an apparatus according to the above objectives which can provide all of the benefits associated with vertical turret lathes and engine lathes simultaneously, thereby eliminating costly secondary operations.

These and other objectives and benefits will be made manifest when considering the following detailed application when taken in conjunction with the drawing figures.

FIG. 1 is a front view of the pipe lathe according to the present invention;

FIG. 2 is a side view thereof;

FIG. 3 is a sectional view taken along lines 3--3 of FIG. 2;

FIG. 4 is a sectional view taken along lines 4--4 of FIG. 1;

FIG. 5 is a perspective view of a mandrel for retaining the lathe within the pipe;

FIG. 6 is a sectional view taken along lines 6--6 of FIG. 5;

FIG. 7 is a detailed perspective view of the left hand side of FIG. 5;

FIG. 8 is a perspective view of a cutting mechanism advancing device;

FIG. 9 is a perspective view of an initalization and one form of indexing mechanism receiving unit for a cutting device.

FIG. 10 is a perspective view of the indexing mechanism sending unit.

FIG. 11 is a perspective view of the external beveling cutter according to the present invention;

FIG. 12 is a front view of the support sling according to the present invention;

FIG. 13 is a perspective view of the external part-off cutter according to the present invention;

FIG. 14 is a perspective view of the internal beveling cutter according to the present invention;

FIG. 15 is a sectional view taken along lines 15--15 of FIG. 14;

FIG. 16 is a sectional view taken along lines 16--16 of FIG. 14;

FIG. 17 is a front view of the indexing sending mechanism shown in FIG. 10;

FIG. 18 is a side view thereof;

FIG. 19 is a fragmentary view of an advancement mechanism for FIG. 14;

FIG. 20 is a perspective view of a second lathe supporting member for external mounting of the lathe upon the pipe;

FIG. 21 is a perspective view of the support shoe shown in FIG. 20 having a different dimension to accommodate pipes of different sizes;

FIG. 22 is a sectional view taken along lines 22--22 of FIG. 21 including an additional member for tightening the shoe onto the outer contour of the pipe.

FIG. 23 is a perspective view of a support carriage adapted to replace the sling of FIG. 12;

FIG. 24 is a rear view of the supporting foot shown in FIG. 23;

FIG. 25 shows the height adjustment mechanism for the support carriage of FIG. 23;

FIG. 26 is a second form of an internal beveling tool to that shown in FIG. 14;

FIG. 27 is a sectional view taken along lines 27--27 of FIG. 26; and

FIG. 28 is a sectional view taken along lines 28--28 of FIG. 26.

Referring to the drawings now, wherein like reference numerals refer to like parts throughout the various drawing figures, reference numeral 10 is directed to the universal pipe lathe according to the present invention.

This lathe can generally be regarded as having a stationary ring 4, a portion of which underlies a second rotating ring 6 (FIGS. 1-4). The rotating ring 6 is supported upon the stationary ring 4 by means of adjustable support rollers 24 freely rotatable within a "V" shaped trackway 26 formed from two symmetrically fashioned pieces. The rollers 24 are capable of replacement and alignment by means of a threaded shaft 25' and locknut 27' provided within a cap area 24' capable of being opened on the rotating ring 6 should the need arise. Non-adjustable rollers (shown in phantom in FIG. 4) are angulated relative to the other rollers shown, and also ride in the trackway in rolling engagement, so that together, axial and radial play are eliminated. At least six rollers are preferred equispaced in pairs.

Preferrably two drive motors which reduce gear tooth load, require smaller gears and increase and distribute torque with no lag, are provided and are capable of excitation by means of hydraulic or pneumatic lines 2 in a manner well known in the art. The motors 1 are supported on the stationary ring 4 by means of an adapter plate 14, the configuration of which is variable to accommodate either type of motor, and depending downwardly from the motor is a shaft 18 which has on its downwardly extending terminus a conically tapered drive gear 20 adapted to mesh with a ring gear 22 fastened on a side face of the rotating ring 6. A housing is provided which isolates the ring gear 22 and the drive gear 20 and is defined by an L-shaped backhousing 28 which terminates with the mounting plate 14 on the top face, and a front wall 12, 8 is provided to occlude external contamination by metal shavings, dirt, water, and conceivably the apparel of the machine operator. To assure complete sealing, the rotating ring 6 is further isolated from the drive area by means of an upper seal 16 extending between the front housing portion 8 and a second seal 16' disposed between the stationary ring 4 and the rotating ring 6 on a front area of the lathe.

The members 4, 6, 8, 22 and 26 are capable of being split so that once open they may straddle a pipe given a situation wherein the pipe is of continuous length and access to an end portion of the pipe is not possible. FIG. 3 details a fastening mechanism preferred in the joining of the split frame member sections. Along a diameter of the rings, both extremities of the diameter have junctures defining the two thus formed member sections pivotable by means of hinge pins 34, the juncture of which is provided with a bifurcated yoke 30 on one section which has interposed therebetween a tongue 32 provided on the other section. Apertures are provided through the yoke and tongue so that when the apertures are in registry, the travel limiting hinge pin 34 can be inserted therethrough in order to pivot the sections of the split frame. Retaining blocks 13 (FIG. 1) are used to affix rings 4 and 6 when the frame is split. In actual use, (FIG. 3) dowels 17 serve to align the sections, bolt 19 provides actual retention, and bolts 15 remove the actual travel (1/2 inch) allowed by pin 34 to clear the dowels 17. FIG. 1 details a cam surface 36 provided flush along the inner periphery of the stationary ring 4 and ear members 38 on an outer periphery of purposes to be defined later.

As stated supra, indexing means are provided which includes at least one cam surface 36 disposed on a side face of the first ring member 4 nearest a second side face 21 (FIG. 3) of the second ring member 6, and it is to be noted that the second ring member 6 rotatably carries thereon follower means 41 (FIG. 10) oriented to travel over the cam surface 36 so as to advance cutting means to be described. Two forms of support bars which extend along a chord of the second ring 6 disposed on holes H (FIG. 1) thereof bear the legend 90a and 90b, FIGS. 11 and 14 and carry some of the various cutting means. Specifically, the follower means 41 includes a follower support block 42 carried on a support bar 90(a), (b) for storage only (when working, block 42 mounts on ring 6). Block 42 has a follower 50 depending therefrom and oriented to engage the cam surface 36, the follower 50 being carried on a follower shaft 58 which is provided with a light torsion spring 56 so that the follower 50 will stay in contact with a plunger 54 through a bell crank 52 at all times including when being rotated by the cam. Follower shaft 58 has fixedly mounted thereon the bell crank 52 oriented to engage a plunger 54 integral with a fluidic master cylinder 45 carried in trunnion block 46 supported on the follower support block 42 by means of a pair of upstanding yoke elements 44 which straddle the trunnion 46 but allow rotation about pivot 47 whose travel is limited by pin 49 in yoke slots 44' to assure registry between bell crank and plunger, this being desireable so as to not damage the plunger, etc., when the machine is reversed.

The fluidic pulse is carried along the fluid containing line 60 and the line terminates and drivably engages cutting means having various configurations disposed on a support block. FIG. 9 shows a typical installation in which the cutting means support block 64 is provided with a second hydraulic cylinder and return spring 61 which are attached to the fluid line 60 and its plunger is axially extendable by the fluidic pulses. A pawl 68 which includes a directional advancing tooth 70 is supported on a pawl mount 66 axially translatable (see arrows) on the cutting means support block 64 so that axial translation of the pawl mount 66 and therefore rotation of the pivoted pawl is possible as it coacts against and advances a ratchet wheel 72 so that the rotation of the ratchet wheel 72 can advance a cutting mechanism driven by the ratchet wheel 72 through lead screw 78. Spring plunger screw 63 operates in detents 65 to keep pawl 68 from rotating out of position. Initializing means are included on the outer face of the ratched wheel which is shown in FIGS. 9 and 11 and comprise a hand crank 76 disposed on an outer face of a knurled hand knob 74. In some cases for facilitating rapid initialization, the crank 76 is extendable radially from the knob 74 by a biased ball 79 and detent system 81 as shown in FIG. 11. That figure depicts a cutting means defined as an external beveling tool and includes a beveling support block 87 carried on the support arm 90a, a tool holder 88 slidably disposed in a dovetailed trackway 84 formed on the support block, and as shown, a removable cutting tool 86 is fastened to too holder 88 by means of screws. FIG. 8 shows how the tool holder 88 is advanced along the length of the lead screw 78, and the lead screw 78 is fastened to the support block portion 64 nearest the ratchet 72 through a thrust collar 82 as shown in FIGS. 8 and 9. The lead screw 78 has a bronze threaded block 80 carried in the tool holder 88 and capable of advancement along the length of the lead screw as the ratchet wheel 72 rotates.

FIG. 13 shows a cutting means defined as an external part-off tool operating on the same mechanical principles as that which is defined in FIG. 11, but the cutting tool bears a different geometrical configuration and accordingly so does the tool holder 88'. Further, whereas the tool holder support block 87 in FIG. 11 has a substantially rectangular configuration, the support block 87' in FIG. 13 defines a substantially "T" shaped block wherein the head or top portion of the "T" tapers towards the base away from the cutting tool. Two or more external part off tools can be simultaneously used: the first for an initial cut, and the second cuts a clearance for the first thereby preventing binding.

With reference now to FIGS. 14, 15, 16, and 19, there is shown an internal beveling cutting means according to one form of the present invention. This device is provided with a cutting means support block 96 carried on the support bar 90b. This internal beveling tool is defined by an indexing wheel 92, a first lead screw 94 (FIG. 16) supported on the block 96 and affixed on one end to the indexing wheel 92, a first dovetail trackway 98 (FIG. 15) formed on the block 96, a slide body 100 having a lower portion disposed in the dovetail trackway and having a threaded block 102 engaging the first lead screw 94 so that rotating the indexing wheel 92 manually extends and retracts the slide body 100 along the length of the first lead screw. The bronze threaded block 102 is similar to that which (80) is shown in FIG. 8. A slide body upper portion 104 which has a second dovetail trackway 105 formed thereon is connected to the lower portion by means of a slide body intermediate portion 106 which has the form of a swivel including an inner lipped cup which frictionally rides within an outer rimmed cup receptive portion so that rotation between the upper and lower portions is possible. A second lead screw 108 is provided and supported by the second dovetail trackway 105 and by means of a threaded sleeve 110 carries a tool holder support plate 112 so that the second lead screw 108 is responsive to the ratchet wheel 72. A tool holder 114 is disposed on the tool holder support plate 112 and a cutting tool 116 is fastened in the tool holder with screws. The tool holder is adapted to translate laterally relative to the longitudinal extent of the second lead screw 108 by means of trackways 118 on the tool holder support plate 112 so that the tool holder can be displaced to one side or the other. FIG. 9 shows and describes the similar advancing system.

Differences between the two support bars 90a and 90b (FIGS. 11 and 14) can now be readily perceived. The first support bar 90a is angulated so as to form a substantially "V" shape configuration whereas the second support bar 90b is linear and is provided with a slot 158 along the central flat outer portion thereof to allow the internal beveling cutting tool to be translated along the length of the slot. Both support bars have a downwardly extending bracing mechanism which, in section, would appear to give the support bar 90 a T-shaped or L-shaped configuration for additional rigidification.

As partially shown in FIG. 14, and further depicted in FIG. 19, the ratchet wheel 72, for clearance reasons, may drivably engage the second lead screw 108 through a first gear 120 connected to the common shaft 122 which first gear 120 then drivably engages a second gear 124 carried on the second lead screw 108.

As shown in FIGS. 17 and 18, the depending portion of the support bar 126 is provided with bores which are adapted to align with holes H on the rotating ring 6 so that the rotation of the ring 6 causes rotation of the cutting element while the indexing element 41 for the cutting operation is removed from storage on 90 and placed on rotating ring 6 contacting cam surface 36. Additional support is provided by an angulated beam 128 extending between the top face 90a, 90b of the support bar and the downwardly extending bracing mechanism 126.

FIGS. 26, 27 and 28 show a second form of the internal beveling machine in which a further intermediate trackway having a dovetail is provided, and additional locking constraints are provided to assure that all types of internal beveling can be effected. Specifically, those parts common to both species bear the same reference numerals but the additional dovetail trackway and advancing mechanism is shown as reference numeral 131 generally. The upper and lower portions and intermediate swivel all bear similar reference numerals to the previously discussed internal beveling tool, and the modifications provide an additional degree of freedom, as well as varied locking mechanism for the dovetail trackway and the support bar 90b as will now be detailed. It is apparent that in FIG. 14 the elongate slot 158 requires that nuts and bolts be loosened in order to translate the internal beveling mechanism along the length of the support bar 90b. With the current mechanism of FIG. 26, this translation can be effected in a manner similar to the dovetail trackway translation defined by the upper portion of the internal beveling attachment. FIG. 27 also provides a further form for the swivel 106 in which it is shown that a downwardly depending inverted "T" shaped rod 152 is disposed in such a manner that rotation of the upper beveling portion 104 relative to the lower beveling portion 100 (FIG. 26) can be expeditiously effected and locked with nut 152'. Further, the mechanism for affixing the tool holder 114 to the tool holder support plate 112 is shown as being a threaded bolt 153 which extends downwardly into the trackway 118 so that the track is firmly affixed between bolt 153 and nut 153'. By tightening the nut 153', the support plate 112 and the tool holder 114 are firmly affixed. Lever 140 is used as a handle to change tool 116. Similarly, the dovetail trackway 98 (FIG. 28) is constrained from displacement not only by the lead screw 94, but also by engagement of the lever 138 against the dovetail trackway 98 through an intermediate element friction pad 136. To further allow the internal beveler to translate along the length of the support bar 90b, a third dovetail trackway 130 is bolted therebetween having abutments 156 at opposed extremities of the dovetail to constrain the motion of the beveler. The lower portion of the cutting means supporting block 96 has a complemental cut away portion to ride on this trackway 130. Similar to the other locking lever 138, further locking levers 142 and 144 are deployed for frictional engagement against the surface of the dovetail trackway 130 as best seen in FIG. 26. The device has a further stop member and support means as shown to the right of FIG. 28 wherein an abutment block 148 is placed in tangential registry with the supporting block 96. The abutment block 148 is connected through threaded micrometer rod 146 to an apertured stop plate 150 supported on slide 132, and on the right hand portion, the rod 146 has a knurled micrometer advancement 134 thereon which allows fine adjustment of the internal beveler along trackway 130 when lock up lever 144 is locked and lever 142 is unlocked.

To assure that any of the compound slide assemblies comprising for example elements 100, 98, 96 of FIG. 28 are accurately fabricated, and very strong, the following technique for a precision sliding fit follows the following method:

Assemble first the slide 100 with the dovetail 98 and hold same in place by means of a set screw 137. The bottom surfaces of these two elements are ground flat simultaneously to provide a zero clearance fit. The dovetail 98 is then removed and a very slight amount is ground off of the slide bottom surface 100 to give a close tolerance fit so that when the dovetail is bolted to the supporting block 96 a very tight interconnection is provided.

In one form of the invention, the pipe lathe is provided with clamping means so that when a continuous pipe section is not accessible at an end portion thereof, the pipe lathe may be split as detailed in the description of FIG. 3, and caused to straddle the pipe as best seen in FIG. 12. In this case a sling is attached to the ears 38 described hereinabove and the sling which in the preferred form is comprised of a triangle having two substantially equal legs 178 of chain or the like, depends from ring 180.

The triangle is made complete by means of a crossbar 182 extending between termini of the legs 178 remote from the ring 180. Downwardly depending chains 184 are hooked to the ears 38 as shown in FIG. 12 so that the pipe lathe can be split and caused to straddle the pipe to be worked on. It should be appreciated that the pin 34 of FIGS. 3 and 12 can serve as the hinge pintle so that both opposed sides of the split sections can be disassembled if so desired. Once the pipe has been circumferentially straddled by the lathe, clamping means are provided in order to support and retain the pipe lathe thereon. FIGS. 20, 21, 22 detail a preferred form of the clamping means in which shoes 160 are provided and interposed between the pipe P and the first ring 4. An adjusting bolt 162 is fastened to and extends through the first ring 4 so that when the bolt is tightened against the shoe 160 the pipe can be fixedly secured to the lathe and adjustment of the adjusting bolt 162 can provide and assure that the pipe is centered therewithin, expecially when four shoes are used. In order to assure centering, at least two such shoes must be present. It is further contemplated that the adjusting bolt 162 is fastened through the first ring 4 by means of a adjusting bolt block housing 176 which is provided on an outer face of the ring 4 so that the bolt extending therethrough can find suitable purchase and ease in adjustment. The bolt 162 may have an annular groove 162' (FIG. 22) for use with a retaining dowel 163 thusly:

The shoe 160 in a preferred form includes a contour bottom surface complemental to the curvature of the pipe P, and a closed slot mechanism 164 which in cross-section (FIG. 22) details a rectangular void having one face thereof open for slidable insertion therein of a space block 166. For this purpose, the space block 166 is provided with inwardly directed grooves 165 to assure sliding contact with the slot 164 as shown. Once in registry, the groove 165 in the spacer block 166 is constrained from lateral displacement along the length of the slot 164 by means of a ball plunger 170 being biased by spring 168 formed within a recess on the spacer block, and the ball plunger registers with a detent 172 provided on the shoe. The recess is shown as 186. A chamfered surface 172' on slot 164 allows ease in sliding the spacer block 166 and ball plunger 170 therein.

When the pipe is capable of engagement from an inner portion of the pipe, for example when the terminus of the pipe extends only a short distance (inches) out from a wall, the pipe can retain the lathe thereon by use of the mandrel depicted in FIGS. 5 through 7. The mandrel can be centered or off centered to work on pipes that are out of round or have differences in wall thickness. As shown therein, the second form of clamping means comprises a tubular mandrel 188 which is partially inserted within the bore of the pipe, and the mandrel is fastened to the bore at one extremity. As shown expecially well in FIG. 6, a cone shaped terminus 190 is provided with trough like guide slots 198 within which are disposed a plurality of outwardly radiating vanes 196 which are provided with notches 202 adapted to receive a spring resilent tensioning member 200. Forward of the vanes there is a plate member 206 having radially extending grooves 204 whose function will be described at this time.

Centrally disposed within the tubular mandrel is shaft 194 having a threaded terminus upon which nut 208 is fixed so that retraction of the shaft 194 in the direction to the right as shown in FIG. 6 will cause the vanes 196 to ride upwardly on the cone so as to allow the vanes to engage the inner portion of the pipe. By appropriate manipulation of nut 210 at the extremity of threaded shaft 194 remote from the terminal disc 206 provided with the grooves 204, the vanes 196 can be appropriately deployed. The other extremity of the mandrel is provided with an annular disc 192 having a portion in threaded engagement with an outer periphery of the tubular mandrel 188, and the threads 214 coact with a handle and support sleeve 212 so that rotation of the sleeve 212 will cause axial translation of the mandrel. It is contemplated that the annular disc 192 can be provided with the shoe retention element (FIG. 20 through 22) discussed supra if the mandrel is to be affixed to the pipe at the outer end of the pipe, these shoes resting on flats 192' and the lathe supported thereon.

A further alternative support to the sling can be found in FIGS. 23 through 25 wherein support means are displayed which includes a stand 216 having a nesting surface 218, 220 complimental to the first stationary ring 4. Adjusting means 222 (FIG. 25) are provided for elevating the nesting surface as required which is defined by a threaded jack 238 that coacts with a worm screw 242 actuated by a shaft 236 connected to crank wheel 246 that extends through a bearing 248, the shaft 236 having a universal joint 244 on the shaft to provide clearance around sleeves 252 and 254. The shelf 234 which serves as the substrate for the nesting surface is affixed to the jack 238 and therefore elevates the nesting surface up and down in coaction with the telescoping sleeves 252 and 254 respectively. The elevating means in turn are supported and carried by a wheeled carriage 224 which is foldable by means of arms 226 having hinges 260 as shown in FIG. 23. Specifically, a pair of angulated upper bracket members 228 and 230 are in hinged relationship so that folding occurs along the front face of the support means, and the hinged arms 226 fold in conjunction therewith so as to allow the stand to require minimum of space when in storage. For added stability, a foot member 250 is provided along a rear back support plate of the carriage, which when downwardly deployed effectively prohibits the stand from unwanted motion.

Having thus described the invention, it should be apparent that numerous structural modifications and adaptations may be resorted to without departing from the spirit of the invention.