Classifications

• • E—FIXED CONSTRUCTIONS
  • E21—EARTH OR ROCK DRILLING; MINING
  • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
  • E21B19/00—Handling rods, casings, tubes or the like outside the borehole, e.g. in the derrick; Apparatus for feeding the rods or cables
  • E21B19/16—Connecting or disconnecting pipe couplings or joints
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
  • B23P—METAL-WORKING NOT OTHERWISE PROVIDED FOR; COMBINED OPERATIONS; UNIVERSAL MACHINE TOOLS
  • B23P19/00—Machines for simply fitting together or separating metal parts or objects, or metal and non-metal parts, whether or not involving some deformation; Tools or devices therefor so far as not provided for in other classes
  • B23P19/04—Machines for simply fitting together or separating metal parts or objects, or metal and non-metal parts, whether or not involving some deformation; Tools or devices therefor so far as not provided for in other classes for assembling or disassembling parts
  • B23P19/06—Screw or nut setting or loosening machines
  • B23P19/061—Screw or nut setting or loosening machines for pipes or pipe-couplings

Definitions

• the invention relates to a method and a device for pressure-tight screwing, in particular a pipe end provided with a conical thread
• the present invention essentially relates to a method and a device which are provided for screwing pipe ends with a connecting sleeve already in the manufacturing workshop in preparation for later use.
• the method according to the invention and the device according to the invention are also suitable for producing other screw connections, provided the requirements are similar there, as for the preliminary screwing of a pipe for a borehole with an associated connecting sleeve.
• the invention can also be used for screwing with cylindrical threads, even if in the following reference is always made to conical threads.
• Conventional pipes for deep drilling have a diameter of approximately 150 mm.
• the device according to the invention should also be usable for pipes of different diameters.
• the torque required for pipes with a diameter of 150 mm and a conical thread for the pressure-tight tightening of the screw connection is approximately 2,500 kpm in order to give an impression of the orders of magnitude to be mastered.
• the holding forces required for this during the production of the screw connection are, depending on the friction between the holding members for the pipe and the pipe surface itself, between approximately 80 and 120 t.
• screw connections can be produced by clamping the pipe end and the sleeve in one of two coaxial chucks, at least one of which can be rotated relative to the other by means of a drive.
• a procedure is unsatisfactory from an economic point of view alone.
• conventional lathe chucks such as those used in machine tools, are not suitable for the intended purpose.
• the invention is therefore based on the object of providing a method and a device which is suitable for carrying out this method and which can be used to produce screw connections of the type mentioned which are technically flawless.
• the task should also include the creation of a special, suitable chuck in the context of a preferred embodiment of the device according to the invention.
• the pipe end is clamped behind its thread in a rotatable pipe chuck with a continuous bore.
• An auxiliary mandrel provided with a thread corresponding to the end of the tube is screwed into one end of the sleeve, while the sleeve is held by a gripping device.
• the sleeve now carried by the auxiliary mandrel is brought into a coaxial position with respect to the clamped pipe end and screwed onto the pipe end by rotating the auxiliary mandrel relatively quickly until a certain torque is reached.
• this can be done by letting the relatively weak drive motor of the auxiliary mandrel rotate until it is stopped by the thread of the screw connection itself.
• a chuck is closed around the sleeve and the auxiliary mandrel
• OMPI ⁇ ⁇ unscrewed from the sleeve is rotated relative to the socket chuck until a torque required to achieve a pressure-tight screw connection is reached.
• This torque can be measured on the non-rotatable sleeve lining.
• chucks are preferably used which, despite the high clamping forces, permit a certain angulation and a certain parallel offset of the clamped pipe or the clamped sleeve to compensate for eccentricities.
• the sleeve can be screwed onto the auxiliary mandrel at a relatively high speed. In a preferred embodiment, this speed is between approximately 200 and 400 revolutions per minute.
• the moving masses for this are small, since they consist solely of the auxiliary mandrel and the rotary drive required for this.
• the means for holding the sleeve during the screwing in of the auxiliary mandrel can be designed in such a way that they have a certain flexibility, so that a certain eccentricity of the sleeve thread does not interfere. After removal of the gripping device provided for this purpose, the sleeve is held exactly centrally with the thread to be screwed onto the pipe end, provided that the threads at both ends are exactly coaxial.
• any eccentricity of the sleeve is eliminated. Only the pipe end can still have a certain eccentricity, which is why the pipe lining should allow a certain lateral displacement of the pipe when the sleeve is screwed on. Since the auxiliary mandrel with the sleeve and not the pipe chuck is rotated for screwing on in a preferred embodiment of the invention the pipe chuck need not be suitable to compensate for a rapidly rotating eccentricity.
• the fast rotating auxiliary mandrel guides the socket thread precisely in the center.
• a pre-screwing of the sleeve by rotation of the auxiliary mandrel also results in this operation that the relatively large mass of the pipe lining does not need to be accelerated, but only the much easier-made auxiliary mandrel. In this way you can easily reach speeds of 200 to 400 revolutions per minute.
• the pre-screwing process is completed when the sleeve is screwed onto the pipe end practically up to the thread stop and further tightening of the screw connection requires a torque which exceeds the torque of the relatively weak auxiliary mandrel drive so that it stops. Since the sleeve is already on the pipe end, the closing of the sleeve lining now taking place can no longer cause a lateral displacement of the sleeve relative to the pipe end as a result of an eccentricity of the sleeve. If such an eccentricity is actually present, it must be absorbed entirely by the flexible execution of the feed.
• the pipe liner can be rotated at a relatively low rotational speed, but with a high torque, in comparison with the sleeve liner which is held in a rotationally fixed manner. There are also no dynamic difficulties due to a possible eccentricity of the tube. At the low speed of rotation, the pipe chuck can adapt to the eccentricity of the pipe, which changes its angle, just as it does in the stationary state when the sleeve is unscrewed.
• the tightening torque is advantageously limited by the signal from a torque sensor, which is connected to the socket lining, which is arranged so as to be rotationally fixed.
• An automatic device operating according to the method according to the invention also offers the possibility of simultaneously screwing a new sleeve onto the auxiliary mandrel and tightening the screw connection. As soon as the auxiliary mandrel is removed from the screwed-on sleeve again, these two work processes can run side by side, as a result of which very high machine performance is achieved.
• a device according to the invention which is suitable for carrying it out is characterized by a screw-pulling device consisting of two spaced-apart, continuous bores with coaxial chucks for high clamping forces, of which at least one is rotatably mounted and provided with a rotary drive for high torque, an auxiliary mandrel arranged in the axial extension of the one clamping chuck or sleeve chuck and provided with a second rotary drive, the end of which facing the sleeve chuck with an end corresponding to the pipe end threaded and of a lining of the Muffen ⁇ position spaced in the axial direction into the socket lining is slidable into it, as well as a gripping device for the sleeve, which eg in the feed W is movable into the auxiliary mandrel. ; ⁇ :
• the pipe chuck is rotatably mounted with a rotary drive, while the socket chuck is also rotatably mounted, but is essentially held in a rotationally fixed manner by a torque measuring device acting on a radial arm.
• the sleeve is
• the lining is designed to be freely displaceable in the axial direction in a certain area, in order to take into account the certain translation movement of the sleeve on the pipe end, even when the displacement is tightened.
• Both the sleeve lining and the pipe lining are in a preferred embodiment designed so that they allow both an axial angular deviation and a certain eccentricity of the workpieces clamped in them. It is expedient to provide the chuck with a device with which it can first be returned to a central starting position before clamping a new workpiece, provided that this does not result from frictional resistance.
• the object of the device part of the invention is therefore also a chuck for high clamping forces for use in the manufacture of pressure-tight pipe fittings, which is provided with hydraulically actuated, concentrically closing clamping jaws.
• the chuck according to the invention consists of an actual chuck body which is rotatably mounted in a bearing ring which is provided with a cardanic suspension. To avoid deformations of the clamped object, these jaws of the chuck are designed in such a way that they grip the clamped object as far as possible along its entire circumference.
• the chuck When the chuck axis is in a horizontal position, the chuck is expediently designed such that the bearing ring is pivotably supported by means of two diametrically opposed, vertical joint pins in corresponding bores of a concentric cardan ring surrounding it at a certain distance, which in turn has two mounted on its outside, diametrically opposite horizontal hinge pin in corresponding bores in the associated part of the machine frame or another support part, wherein
• both the vertical and the horizontal hinge pins have such an axial play that the chuck body can move with a certain play in the vertical direction and the gimbal with a certain play in the horizontal direction.
• two adjusting pistons are preferably provided in the machine frame, which act on the pivot pins of the gimbal.
• only one actuating piston is required, which is preferably on the lower one
• the hinge pin of the chuck body attacks. So that the chuck body does not constantly sink into an eccentric position due to its own weight, the lower hinge pin is additionally supported by a compression spring, which has approximately the own weight of the chuck body and the parts movable with it, including the own weight of the clamped one Compensates for the workpiece.
• the chuck can grasp the clamped workpiece as much as possible, it is preferably equipped with eight clamping jaws.
• the individual clamping jaws have an axial extent which is preferably several times greater than their width in the circumferential direction.
• the force-applying feed elements expediently only engage at a central point or in the direction of only a central circumferential line on the rear side of each clamping jaw, so that the clamping jaws can move through a certain angle in their radial plane in order to move as uniformly as possible to the surface of the clamped workpiece.
• the feeder element can also take the jaws back when the chuck is opened, they are to a certain extent articulated to the back of the jaws. This can be done, for example, with a hammer head
• Tappets are made on the feed element, the wings of which lie in a plane perpendicular to the chuck axis and behind grasp the edges of a groove that leads at least from one end face of the clamping jaw to its center. The clamping jaw can thus be pushed onto the feed element from the side.
• the force-applying feed elements themselves are designed as hydraulic clamping cylinders with hydraulic pistons acting on one side in the closing direction of the chuck.
• the pistons are reset when the pressure is released by a return spring.
• This embodiment has the advantage that the closing movement of the clamping jaws takes place relatively evenly and concentrically after the restoring force of these return springs has been overcome by the pistons. Without overcoming the spring force, the use of the closing movement while connected to a hydraulic system on the random size of the 'frictional resistances in the individual cylinders would be dependent.
• each piston receives the same pressure, but is not rigid due to the incompressibility of the hydraulic fluid, but can to some extent avoid unevenness.
• Figure 1 is a plan view of a device according to the invention in a schematic representation.
• FIG. 3 shows a section approximately along the line III-III in FIG. 2 through the actual design of a chuck according to the invention.
• Fig. 1 consists of an indicated only by certain fixed points Maschinenrah ⁇ men 1, in which a tubularly 2 Agern means Kugell '3 is mounted mos ⁇ bar tter.
• a pipe 4 is clamped into the pipe chuck, the pipe end 5 of which is provided with a conical thread.
• a gear 6 is connected to the pipe chuck 2, which meshes with a gear 7 which is driven by a stationary drive motor 8.
• the drive chain 8, 7, 6 is only indicated schematically as such. In an actual embodiment, it can be designed substantially differently.
• a sleeve chuck 9 is arranged coaxially with this, which consists of an actual chuck body 10, which contains the clamping jaws not shown in FIG. 1 and their feed elements, which in one via ball bearings 11 non-rotatable, ring-like component 12 is mounted, which, as will be described below with reference to a special embodiment, can contain a gimbal.
• the entire sleeve lining 9 is axially displaceable in a certain area in a guide 13, in order to be able to follow the pipe end 5 in its translational displacement when the sleeve 14 is tightened.
• actuators are additionally provided, with which the sleeve lining 9 can be returned to an axial starting position.
• the chuck body 10 is provided with a radially 'outward facing arm 15, which bears against a ab ⁇ attached to the construction part 12 torque measuring device 16, which may be, for example be ⁇ a load cell.
• the chuck body 10 of the sleeve chuck 9 is only supported in the ball bearings 11 for this purpose. Since the arm 15 only carries out very short measuring paths, the entire sleeve chuck 9 is designed to be practically non-rotatable despite the rotatable mounting.
• ge ge gripping arm 17 On the pipe chuck 2 facing away from the sleeve chuck 9 is a pivoted in the machine frame 1 ge ge gripping arm 17 is arranged, which is provided at its end with a gripping device 18 which in the Ve extension of the axis of the two chucks pivotable in the schematic representation of the Fig. 1, the G arm 17 is shown as it holds a further sleeve 14 'coaxially with the axis of the two chucks 2 and 9.
• a Hil mandrel 19 is arranged on the side facing away from the pipe chuck 2, which is provided with a threaded end 20 which corresponds to the pipe end 5.
• the Gewi deende 20 is expediently interchangeable with such other diameters and other threads for processing different pipes.
• the extended axis de auxiliary mandrel 19 is provided with a drive gear 21
• the auxiliary mandrel 19 itself is rotatably mounted in a slide 22 bar, which is movable in the axial direction in the machine frame 1.
• a further motor 23 is fixedly mounted on the carriage 22, which drives a gearwheel which meshes with the drive gearwheel 21 of the auxiliary mandrel 19.
• In the machine frame 1 there is also an actuating cylinder 25 with which the slide 22 can be moved axially in the machine frame 1.
• the device works as follows: The gripping arm 17 takes over a sleeve 14 'in the locked state from an automatic feed device (not shown) and swivels it into the extended axis of the movable auxiliary mandrel 19, which coincides with the axis of the chucks 2 and 9. Then the auxiliary mandrel 19 is moved by means of the actuating cylinder 25 with its threaded head 20 to the sleeve 14 'and set in rotation by the motor 23 via the drive chain 24, 21, so that the threaded head 20 screws into the sleeve 14'.
• the carriage 22 is tracked.
• the motor 23 is automatically stopped, for example by a torque control.
• the gripping force of the gripping device 18 of the gripping arm 17 must be somewhat greater than that force which is generated by the full torque of the motor 23 in the threaded head 20 of the auxiliary mandrel 19.
• the gripping arm 17 can now pivot a new sleeve 14 'in front of the threaded head 20 of the auxiliary mandrel 19, so that the process described so far can run again.
• the motor 8 After gripping the sleeve 14 by the sleeve chuck 9, the motor 8 is put into operation and starts the pipe chuck 2 via the toothed wheels 7 and 6 to tighten the screw connection between the sleeve 14 and the pipe end 5, but relatively slowly, but with a large moment to turn.
• the torque applied to the screw connection is continuously measured via the arm 15 and the measuring device 16 of the socket lining 9.
• the motor 8 switches off automatically.
• FIG. 2 shows a schematic front view of the structure of a socket lining according to the invention, as is preferably used in a device according to FIG. 1.
• the figure shows the actual chuck body 10 in which a sleeve 14 is held by eight clamping jaws 26.
• the chuck body 10 is in one via a ball bearing 11 '
• the assembly 12 ' contains a cardanic suspension and in particular consists of a bearing ring 27 which is rotatably mounted in a cardan ring 30 by means of diametrically opposed, vertical pivot pins 28 and 29.
• the gimbal 30 is in turn pivotally mounted in frame parts 32 by means of two horizontal pivot pins 31, which can be displaced in the axial direction via guides 13 'in the machine frame 1.
• the pivot pins 28, 29 and 32 are displaceable relative to their associated bearing bores with a certain amount of play in the direction of their own axes, so that the bearing ring 27 can be moved back and forth in the gimbal ring 30 in the vertical direction by a certain amount and the gimbal ring 30 accordingly opposite the Frame parts 32 in the horizontal direction.
• the resulting play of the chuck body 10 in the radial direction serves to compensate for inaccuracies in the individual sleeve dimensions which would otherwise lead to an eccentric clamping.
• the articulated bolt 29 is supported against a compression spring 33 which is intended to compensate for the inherent weight of the chuck body, the bearing ring and the clamped sleeve.
• return pistons 34 are provided, the piston rods of which can be moved against the pivot pins 29 and 31, respectively.
• the pipe liner 2 of a device according to FIG. 1 can be constructed in a similar manner to the sleeve liner shown in FIG. 2. In this case, however, the guides 13 ', the arm 15' and the torque measuring device 16 'of the chuck of FIG. 2 would be omitted. Instead, the chuck body 10 would have to be provided with a rotary drive.
• FIG. 3 shows a radial section through the chuck body and bearing ring of a chuck according to the invention, which can be laid approximately along the line III-III of the schematic representation of FIG. 2.
• FIG. 3 The components forming a bearing ring can be seen in FIG. 3, in which the components 10 'of the chuck body are rotatably mounted via a ball bearing 11 ", in which the clamping jaws 26 are guided for a radial reciprocating movement, but of which only one is shown, on the back of the clamping jaw 26 a hydraulic cylinder is arranged inside the chuck body 10 ', consisting of a cylinder jacket 35 and a cylinder cover 36.
• a piston 37 is arranged in the cylinder jacket 35 so that it can be moved back and forth Piston 37 is provided with a piston extension 38 of smaller diameter, which carries at its end a hammer head 39 which engages in a corresponding hammer head groove 40 on the back of the clamping jaw 26.
• the individual parts of the hydraulic cylinder are sealed off from one another by seals 41 Between the piston 37 and the cylinder cover 36 there is the pressure chamber 42, which has a connection 43 for the hydraulic fluids is provided. On its side facing away from the cylinder cover 36, the piston 37 is supported against return springs 44 embedded in the cylinder jacket 35.
• the piston extension 38 is slightly rounded at its end 45, with which it bears against the back of the clamping jaw 26. This is intended to have the effect that the clamping jaw 26 is in constant contact with the piston extension 38 in its radial plane by a certain amount Angle can be tilted so that the entire length of the clamped object can be applied to it even in the event of surface irregularities.
• the individual hydraulic cylinders forming the force-applying feed elements of the clamping jaws are connected to one another in terms of flow and to a pressure compensation tank (not shown).
• a pressure compensation tank not shown.
• the single-acting design of the cylinders with a return spring has the advantage that the closing movement of all clamping jaws starts practically simultaneously after overcoming the return forces of the springs 44 and does not depend on the random frictional relationships in the individual cylinders. As a result, the clamping jaws 26 are closed concentrically.
• the chuck according to the invention can also easily adapt to irregularities of the clamped pipe or the clamped sleeve without the application of force and the transmission of force for the screwing process high torque is affected.

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• Engineering & Computer Science (AREA)
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• Mechanical Engineering (AREA)
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• Physics & Mathematics (AREA)
• Environmental & Geological Engineering (AREA)
• Fluid Mechanics (AREA)
• General Life Sciences & Earth Sciences (AREA)
• Geochemistry & Mineralogy (AREA)
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• 1978
  • 1978-03-03 DE DE19782809110 patent/DE2809110A1/de active Pending
• 1979
  • 1979-03-01 DK DK86279A patent/DK86279A/da unknown
  • 1979-03-02 ZA ZA79988A patent/ZA79988B/xx unknown
  • 1979-03-02 NO NO790715A patent/NO790715L/no unknown
  • 1979-03-02 WO PCT/DE1979/000024 patent/WO1979000704A1/de unknown
  • 1979-03-02 JP JP50055779A patent/JPS55500159A/ja active Pending
  • 1979-05-10 BE BE2/57781A patent/BE876152A/xx unknown
  • 1979-09-25 EP EP79900321A patent/EP0015931A1/de not_active Withdrawn

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