DOWNHOLE CUTTING TOOL

Abstract

A rotary tool for milling tubing in a borehole comprises at least one cutter with a cutter body and a cutting surface on the body. Each cutter is shaped and positioned on the tool so as to reduce tensile stress in the cutter, thereby reducing risk of the cutter becoming chipped or broken in use and produces swarf of reduced rigidity, less likely to form a blockage in the borehole.

Claims

1. A rotary tool for milling tubing in a borehole, the rotary tool comprising: at least one cutter with a cutter body and a cutting surface on the body, wherein the cutter is shaped and positioned on the rotary tool such that at least part of the cutting surface is back raked relative to a direction of rotation so that the cutting surface cuts furthest into the tubing at an edge which is a trailing edge of the cutting surface relative to the direction of rotation, and wherein at least part of the back raked cutting surface extends from the edge with a rake angle between the cutting surface and a perpendicular to the direction of rotation which is in a range from 15 to 60 degrees and, at the edge of the cutting surface, has an angle greater than 90 degrees included between the cutting surface and the surface of the cutter body following the cutting surface.

2. The rotary tool of claim 1 wherein the at least part of the back raked cutting surface extends from the edge with a rake angle which is in a range from 20 to 50 degrees.

3. The rotary tool of claim 1 wherein, at the edge, the surface of the cutter body following the at least part of the back raked cutting surface diverges from the cutting surface at an angle of between 0 and 15 degrees to the direction of rotation.

4. The rotary tool of claim 1 wherein the at least part of the back raked cutting surface extends from the edge with a rake angle which is in a range from 20 to 60 degrees and has an angle of at least 100 degrees included between the at least part of the back raked cutting surface and the surface of the cutter body following the cutting surface.

5. The rotary tool of claim 1 wherein the at least one cutter comprises a cutter body of a hard material.

6. The rotary tool of claim 5 wherein the hard material has a Knoop hardness of 1800 or more.

7. The rotary tool of claim 1, further comprising: a central structure for insertion axially into the tubing, and at least one element which carries the at least one cutter and which projects or is extensible from the central structure to bring the at least one cutter into contact with the tubing.

8. The rotary tool of claim 7 wherein the at least one element is configured to bring the at least one cutter into contact with an internal surface of the tubing to cut radially outwardly into the tubing.

9. The rotary tool of claim 7 wherein the at least one element has the at least one cutter with the cutter body partially embedded therein and partially exposed, such that the embedded portion of the cutter body is of greater volume than the exposed portion.

10. The rotary tool of claim 9 wherein the at least one cutter has an exposed front and a partially embedded thickness following the exposed front with an extent which is at least half the length of any dimension across the cutter body, perpendicular to the partially embedded thickness.

11. The rotary tool of claim 7 wherein the rotary tool has a plurality of elements which each carry at least one cutter formed of hard material, which project or are extensible from the tool body and which are distributed azimuthally around a longitudinal axis of the rotary tool.

12. A method of removing a length of tubing in a borehole, the method comprising: inserting into the tubing a rotary tool for milling tubing in a borehole, the rotary tool comprising at least one cutter as defined in claim 1, and advancing the rotary tool axially while rotating the rotary tool with the at least one cutter cutting into the tubing completely around the tubing.

13. The method of claim 12 wherein the at least one cutter is carried by at least one element configured to bring the at least one cutter into contact with an internal surface of the tubing, whereby the at least one cutter cuts radially outwardly into the internal surface completely around the tubing.

Description

BRIEF DESCRIPTION OF DRAWINGS

[0020] FIG. 1 diagrammatically illustrates a hard cutter carried on a rotary tool and in contact with tubing;

[0021] FIG. 2 shows equivalent stress distributed within a workpiece, in the direction of traverse of a cutter, as predicted by finite element analysis, when the cutter has zero rake angle;

[0022] FIG. 3 shows equivalent stress distributed within a workpiece when the cutter has a rake angle of 30 degrees and when overall force between workpiece and cutter is maximum;

[0023] FIG. 4 is similar to FIG. 3 but shows the distribution of equivalent stress when overall force between workpiece and cutter is minimum;

[0024] FIGS. 5 and 6 are similar to FIGS. 3 and 4, with a cutter rake angle of 45 degrees;

[0025] FIG. 7 is similar to FIG. 3 with a cutter rake angle of 15 degrees;

[0026] FIG. 8 is similar to FIG. 4 with a cutter rake angle of 15 degrees, but shown at a larger scale;

[0027] FIG. 9 diagrammatically shows a piece of swarf produced by a cutter with rake angle of 45 degrees;

[0028] FIG. 10 is an enlarged cross section through a piece of swarf produced by a cutter with rake angle of 45 degrees;

[0029] FIG. 11 is an enlarged cross section through a piece of swarf produced by a cutter with zero rake angle;

[0030] FIGS. 12 to 15 show distribution of principal tensile stress within cutters with rake angles of zero, 15, 30 and 45 degrees respectively, as predicted by finite stress analysis;

[0031] FIGS. 16, 17 and 18 are front and side views of cutters;

[0032] FIG. 19 shows a section mill with a cutter assembly retracted;

[0033] FIG. 20 is a cross section on line A-A of FIG. 19;

[0034] FIG. 21 shows the section mill of FIG. 19 with the cutter assembly extended;

[0035] FIG. 22 is a cross-sectional elevation view of another embodiment of expandable tool, showing its expandable cutter blocks in retracted position;

[0036] FIG. 23 is a cross-sectional elevation view of the expandable tool of FIG. 19, showing the cutter blocks in expanded position;

[0037] FIG. 24 is a perspective view of a cutter block for the expandable tool of FIGS. 22 and 23;

[0038] FIG. 25 shows the cutter block of FIG. 24 in use;

[0039] FIG. 26 is a cross section on line B-B of FIG. 25; and

[0040] FIG. 27 is an enlarged detail from FIG. 25.

DETAILED DESCRIPTION

[0041] FIG. 1 shows part of the body of a cutter 10 which is carried on supporting structure (not seen in this enlarged diagram) which is part of a rotary tool and brings the cutter body 10 into contact with the inside wall of tubing 12 so that part of the tubing is cut away as the cutter is driven in the direction of rotation of the tool around its axis, indicated by the chain dotted arrow 14. The direction of rotation is of course perpendicular to a radius 16 extending from the tool axis.

[0042] The cutter body has a flat front face 20 and a side surface 22 which extends backwards relative to the direction of rotation, connected by bevelled face 24 which constitutes the cutting surface. The edge 26 of the cutting surface, cutting most deeply into the tubing 12, is trailing relative to the parts of the cutting surface 24 which are not in contact with tubing 12. The cutting surface 24 is thus positioned with a back rake angle. The rake angle between the cutting surface 24 and the radius 16 is indicated 34. The angle between the cutting surface 24 and the direction of rotation 14 is indicated 32.

[0043] The side surface 22 of the cutter body 10, extending back from the edge 26 of the cutting surface 24, is inclined so as to diverge from the newly-cut surface at a small angle 36 to the direction of rotation 16, so that the parts of the cutter body 10 behind the cutting surface 24 do not contact the freshly cut surface 28 on the tubing 12. The overall included angle between the cutting surface 24 and the side surface 22 extending back from the edge 26 is the sum of the angles 34 and 38.

[0044] In accordance with the concepts set out above, the angle between the cutting surface 24 and the radius 16 lies in a range from 15 to 60 degrees. The sum of the angles 32 and 34 is a right angle, because the direction of rotation 14 and the radius 16 are perpendicular. Thus the angle 32 lies in a range from 30 to 75 degrees. In the embodiment illustrated the rake angle 34 lies in a narrower range from 20 to 50 degrees and may be approximately 30 degrees.

[0045] The behaviour of a cutter made of hard material cutting into steel, with variations in rake angle, was investigated by finite element analysis, which is a computational modelling procedure, assuming a constant depth of cut of 0.25 mm and a constant speed of traverse of the tool relative to the steel workpiece of 1 metre/sec. The analysis ran for a period of 1 millisecond corresponding to a distance traversed of 1 mm which is four times the depth of cut. This analysis predicted that as the rake angle of the tool is increased (and consequently the angle between the cutting surface and the direction of traverse decreases) the force required to drive the tool increases and moreover with angles of 15 degrees or more the force oscillates between upper and lower values. The values predicted by this procedure were:

TABLE-US-00001 In direction of Perpendicular to traverse traverse Mean Amplitude of Mean Amplitude of Mean Rake force oscillation force oscillation period of angle (kN) (kN) (kN) (kN) oscillation zero 1.9 0.1 0.2 0.1 <0.1 15 2.3 0.2 0.8 0.2 0.1 30 2.6 0.5 1.75 0.25 0.2 45 2.75 0.75 2.8 0.8 0.6

[0046] This analysis also provided visual maps of the workpiece showing internal distribution of the equivalent stress in the direction of traverse. Such maps are shown by FIGS. 2 to 8. In FIGS. 2 to 7 areas 40 with lighter shading have equivalent stress between 730 MPa and 1150 MPa, areas with heavier shading have equivalent stress in a range from 1150 MPa to 1250 MPa and areas of the workpiece shown without shading are subjected to equivalent stress of less than 730 MPa. (FIG. 8 has larger scale and slightly different presentation as will be mentioned below). The stress results in strain and these maps of the workpiece show deformation of material by the cutter.

[0047] FIG. 2 exemplifies the distribution of stress when the rake angle of the cutter 10 is zero. The distribution of stress varied during the length of time covered by the analysis, but a region 42 of highest stress between the arrows 44 was present throughout the duration of the analysis.

[0048] FIGS. 3 and 4 show the predicted distribution of stress when the rake angle was 30 degrees. FIG. 3 shows the predicted distribution when applied force in the direction of traverse was at the maximum (2.6+0.5=3.1 kN) and FIG. 4 shows the predicted distribution when applied force was at the minimum (2.6-0.5=2.1 kN). As shown in FIG. 3, when the force in the direction of traverse is at a maximum, there is a region 42 of highest stress between the areas 44. By contrast, when the force in the direction of traverse is at a minimum, not only is the stress within the workpiece 12 generally lower, there is also a localised region 46 of stress below 730 MPa along a line between arrows 44.

[0049] The interpretation of the oscillation in applied force, tabulated above, and the finite element analysis shown by FIGS. 2-4 is that with zero cutter rake angle, equivalent stress in the workpiece 12 remains fairly constant and the material which is cut from the workpiece (the so-called chip) remains as a continuous strand even though it undergoes plastic deformation as it is cut. By contrast, with the 30 degree rake angle, stress and strain in the region of the workpiece 12 between arrows 44 increase until thermal softening of the material (resulting from plastic deformation causing a localised increase in temperature within the workpiece) enables a region of reduced stress between arrows 44 to propagate from the edge of the cutter to the free surface of the workpiece. When this thermally softened region has fully propagated, the chip being cut is displaced. This gives a temporary reduction of stress in the workpiece 12 and the region 46 of low stress between the arrows 44. Thus the chip becomes separated from the workpiece along the line between arrows 44.

[0050] FIGS. 5 and 6 show the predicted distribution of stress when the cutter rake angle was 45 degrees and applied force in the direction of traverse was at the maximum (3.5 kN) and minimum (2.0 kN) respectively. FIG. 5 shows a region 42 with the high level of stress located between the arrows 44 when the applied force in the direction of traverse is at the maximum, and (similarly to FIG. 4) a region 47 with low level of stress extending along the line between arrows 44, which is where the chip separates from the workpiece 12.

[0051] FIGS. 7 and 8 show the distribution of stress predicted by finite element analysis when the cutter rake angle was 15 degrees and applied transverse force between cutter and workpiece was maximum and minimum respectively. There was qualitative similarity to the maps at cutter rake angles of 30 and 45 degrees. As shown by FIG. 7, when applied force in the direction of traverse was at the maximum (2.3+0.2=2.5 kN) there was a region of high equivalent stress 42 between the arrows 44. FIG. 8 shows the distribution of stress when the applied force in the direction of traverse was at the minimum (2.30.2=2.1 kN). This drawing is at a larger scale than FIGS. 2 to 7. Areas of light shading 41 have stress between 730 MPa and 1000 MPa. Areas 43 have stress between 1000 MPa and 1150 MPa. Areas 42 have stress between 1150 MPa and 1250 MPa. FIG. 8 shows that when applied force in the direction of traverse was at the minimum, a region 48 of stress not exceeding 1000 MPa extends along the line between the arrows 45, in between areas 43 of stress exceeding 1000 MPa within which there were regions 42 of higher stress. Levels of stress within the region 48 were almost all below 900 MPa.

[0052] The predictions of finite element analysis shown by FIGS. 5 and 6 were confirmed by experiment. A cutter as illustrated by FIG. 1, with a rake angle of 45 degrees was used to cut material from a steel workpiece. The chip took the form shown diagramatically by FIG. 9. It consisted of a ribbon of short sections 50 weakly joined one to the next along lines 52. Each of these lines 52 correspond to the instant when a section 50 detached from the workpiece 12 and the localised heating of the displaced material allowed a weak weld to form between adjacent sections 50. A piece of the swarf was embedded in rigid resin, then cut through, polished and photographed under high magnification. This photograph showed a cross section of the swarf along a line such as line X-X in FIG. 9. The photograph was digitally manipulated to show the edge of the swarf: the result is shown as FIG. 10. A double headed arrow shows a distance of 0.1 mm. As a comparison, a piece of swarf obtained with a cutter of zero rake angle was likewise embedded in rigid resin, cut through, polished and photographed under high magnification. This photograph was likewise digitally manipulated to show the edge of the swarf: the result is shown as FIG. 11. It can be seen that the swarf in FIG. 11 was a continuous strip whereas the swarf in FIG. 10 consisted of a number of sections 50, partially separated by gaps 54 so that the joins between the sections 50 do not extend across the full thickness of the piece of swarf.

[0053] Finite element analysis was also applied to stress within the cutters, as shown by FIGS. 12 to 14. Each of these illustrates the distribution of maximum principal tensile stress (the scalar value of maximum tensile stress regardless of direction). Regions 56 where the tensile stress exceeds 100 MPa are shown with shading. In the case of the cutter with zero rake angle shown by FIG. 12 the region 56 included a small region 58 adjoining the cutting surface in which the principal stress was from 300 MPa up to 370 MPa. For the cutter with rake angle of 15 degrees so that the included angle at edge 26 is 100 degrees, the area 56 as shown by FIG. 13 had maximum stress of 230 MPa. In the case of the cutters with 30 and 45 degree cutter rake angles, such that the included angles at the edge 26 were 115 and 130 degrees the principal stress in the areas 56 did not exceed 170 MPa and 130 MPa respectively. Cutter breakage is likely to start where material is under tension and so the lowering of tensile stress with increasing rake angle is valuable because it reduces the risk of cutter breakage during use. In addition, a larger included angle results in a stronger edge and longer tool life.

[0054] FIGS. 16, 17 and 18 show three embodiments of cutters. FIGS. 16a, 17a and 18a are front views, FIGS. 16b, 17b and 18b are side views. The cutter of FIG. 16 is rectangular. A cutting surface 60 at an angle of 30 degrees to the front face 61 extends to the edge 62 which, when the cutter is mounted on a tool, is the edge where the cutter is furthest into the material being cut. The angle included at edge 62 is 120 degrees. The cutter of FIG. 17 has a cylindrical body 63 and a front face 64 with smaller diameter surrounded by an annular surface 65 at an angle of 45 degrees to the front face 64. When mounted on a tool, part of this annular surface 65 is the cutting surface. The angle included between the side wall of the cutter body 63 and the surface 65 is 135 degrees, as shown. The thickness of the cutter behind the front face is indicated at 66 and the cross section transverse to the thickness, which in this case is the diameter of the cylindrical cutter body 63, is indicated 67. In this embodiment shown here, the thickness dimension 66 is about 0.8 of the cross section 67.

[0055] FIG. 18 shows a cutter which also has a cylindrical body, but has a front face 64 which is eccentric relative to the main body. The widest part 68 of the annular surface around the front face 64 is at an angle of 45 degrees to the front face 64 but the narrowest part 69 is at a different angle, as can be seen in the drawing. This cutter is mounted in a tool so that wider parts of the annular surface provide the cutting surface.

[0056] These cutters are made of a hard material which may be tungsten carbide. This hard material may be provided as a powder which is compacted into the shape of the cutter and then sintered. Manufacturers of sintered tungsten carbide cutters include Cutting and Wear Resistant Developments Ltd, Sheffield, England and Hallamshire Hard Metal Products Ltd, Rotherham, England.

[0057] Tungsten carbide is commonly used for cutters because it is very hard and also has good thermal stability. Other hard materials which may be used are carbides of other transition metals, such as vanadium, chromium, titanium, tantalum and niobium. Silicon, boron and aluminium carbides are also hard carbides. Some other hard materials are boron nitride and aluminium boride. A hard material (which is other than diamond) may have a hardness of 1800 or more on the Knoop scale or a hardness of 9 or more on the original Mohs scale (where diamond has a Mohs hardness of 10).

[0058] FIGS. 19 to 21 show a section mill used to remove a length of tubing, starting at a subterranean location which is some way down a borehole. An existing borehole is lined with tubing 72 (the wellbore casing) and cement 74 has been placed between the casing and the surrounding rock formation. The tubing and cement may have been in place for some years. It is now required to remove a length of tubing, starting at a point below ground. One possible circumstance in which this may be required is when a borehole is to be abandoned, and regulatory requirements necessitate removal of a length of tubing and surrounding cement in order to put a sealing plug in place.

[0059] FIGS. 19 and 21 are cross-sectional elevations showing part of the tool to the right of chain dotted centre line CL-CL. FIG. 20 is a schematic cross section looking along the tool axis at the level of the arrows A-A in FIG. 19, with plunger head 91 omitted. As shown by FIG. 19, the tool has a cylindrical body with an outer wall 80. Three slots are formed in this body at positions which coincide axially and distributed azimuthally around the tool axis. At either side of each slot there is a plate 81 extending inwardly from the wall 80. A cutter assembly, which comprises cutters attached to an arm 82 made of steel plate, is accommodated within each slot. As can be seen from FIG. 19, each arm 82 is pivoted to swing around a pin 83 supported by the plates 81. Each arm 82 can swing from a retracted position shown in FIG. 19 to an expanded position shown in FIG. 21. Expansion is brought about by a hydraulic cylinder and piston, not shown, operated by pressure of drilling fluid and connected to drive plunger shaft 89. Pressure of drilling fluid causes the plunger shaft 89 to move downwardly. A domed plunger head 91 on the end of shaft 89 acts on the inside edges of arms 82, forcing each arm to pivot outwardly towards the position shown in FIG. 21. Outward expansion is limited by prolongations 92 of the arms 82 when these prolongations abut the inside face of the tool wall 80 as indicated at 93 on FIG. 21.

[0060] Each arm 82 has cutters 86, 87 of the type shown by FIG. 16 attached to its front face as seen in FIGS. 19 and 21 with the edges 62 of these cutters aligned with the edges 84, 85 of the arm 82. The cutters 86, 87 may be attached to the arm 82 by brazing and when attached to the arm 82 the cutting surfaces 60 of the cutters have a back rake of 30 degrees. At the corner of the arm 82 there is a cutter 88 which extends around the curve between the edges 84, 85 of the arm 82 and has a cutting surface with the same back rake of 30 degrees which also follows around the curve.

[0061] For use the section mill is included in a drill string and lowered to the point within the borehole tubing 72 where milling is to begin. The drill string is then rotated and the plunger head 91 is driven downwards forcing the arms 82 outwards towards the position shown by FIG. 21. The cutters 87 on the outer edges 85 of the arms 82 cut radially outwards into and through the tubing 72 until the arms are fully extended as shown in FIG. 21. The tool is then advanced axially downwards and the cutters 86 on the edge 84 progressively cut downwards into an end face on the tubing 72, destroying a length of the tubing by milling it to swarf.

[0062] As the cutters 86 on an arm 82 cut into the tubing 72, their cutting surfaces are at an angle of 30 degrees to the plane of the arm 82. This arm extends axially and the axial direction is perpendicular to the rotational direction of the tool and to the end face of the tubing 72 which is being cut. The cutters therefore are at a back rake of 30 degrees as they cut into the tubing 72. Previously, as the cutters 87 were cutting into the inside face of the tubing 72, they also were at a back rake relative to the inside surface of the tubing, although the back rake angle relative to this surface will vary as the arms swing around their pivots 83.

[0063] FIGS. 22 to 26 show a rotary tool which is an expandable milling tool, utilising an expansion mechanism which is already used in reamers. FIG. 22 shows the tool with its expandable cutter blocks with the blocks in retracted position. FIG. 23 is a corresponding view with the blocks in expanded position.

[0064] This expandable tool comprises a generally cylindrical tool body 106 with a central flowbore 108 for drilling fluid. The tool body 106 includes upper 110 and lower 112 connection portions for connecting the tool into a drilling assembly. Intermediately between these connection portions 110, 112 there are three recesses 116 formed in the body 106 and spaced apart at 120 degrees intervals azimuthally around the axis of the tool.

[0065] Each recess 116 accommodates a cutter block 122 in its retracted position. The three cutter blocks may be identical in construction and dimensions. One such cutter block 122 is shown in perspective in FIG. 24. Each block 122 is formed of a steel inner block part 124 with a projecting lug 125 along its outer surface and an outer block part 126 astride the lug 125 and bolted to the inner part 124 by bolts (not shown) inserted through the apertures 128 into threaded holes in the inner part 124. Details of the outer part 126 are not shown in FIGS. 22 and 23 and will be described in more detail below. The radially outer face 129 of the outer block part 126 is indicated without detail in FIGS. 22 and 23.

[0066] The inner block part 124 has side faces with protruding ribs 117 which extend at an angle to the tool axis. These ribs 117 engage in channels 118 at the sides of a recess 116 and this arrangement constrains motion of each cutter block such that when the block 122 is pushed upwardly relative to the tool body 106, it also moves radially outwardly towards the position shown in FIG. 23 in which the blocks 122 project outwardly from the tool body 106. The ribs 117 in channels 118 allow each cutter block to move bodily upwardly and outwardly in this way without changing its orientation (i.e. without changing its angular position) relative to the tool axis.

[0067] A spring 136 biases the block 122 downwards to the retracted position seen in FIG. 22. The biasing spring 136 is disposed within a spring cavity 138 and covered by a spring retainer 140 which is locked in position by an upper cap 142. A stop ring 144 is provided at the lower end of spring 136 to keep the spring in position.

[0068] Below the moveable blocks 122, a drive ring 146 is provided that includes one or more nozzles 148. An actuating piston 130 that forms a piston cavity 132 is attached to the drive ring 146. The piston 130 is able to move axially within the tool. An inner mandrel 150 is the innermost component within the tool, and it slidingly engages a lower retainer 170 at 172. The lower retainer 170 includes ports 174 that allow drilling fluid to flow from the flowbore 108 into the piston chamber 132 to actuate the piston 130.

[0069] The piston 130 sealingly engages the inner mandrel 150 at 152, and sealingly engages the body 106 at 134. A lower cap 180 provides a stop for the downward axial movement of piston 130. This cap 180 is threadedly connected to the body 106 and to the lower retainer 170 at 182, 184, respectively. Sealing engagement is provided at 186 between the lower cap 180 and the body 106.

[0070] A threaded connection is provided at 156 between the upper cap 142 and the inner mandrel 150 and at 158 between the upper cap 142 and body 106. The upper cap 142 sealingly engages the body 106 at 160, and sealingly engages the inner mandrel 150 at 162 and 164.

[0071] In order to expand the blocks 122, drilling fluid is directed to flow downwards in flowbore 108. It flows along path 190, through ports 174 in the lower retainer 170 and along path 192 into the piston chamber 132. The differential pressure between the fluid in the flowbore 108 and the fluid in the borehole annulus surrounding tool causes the piston 130 to move axially upwardly from the position shown in FIG. 22 to the position shown in FIG. 23. A portion of the flow can pass through the piston chamber 132 and through nozzles 148 to the annulus as the cutter blocks start to expand. As the piston 130 moves axially upwardly, it urges the drive ring 146 axially upwardly against the blocks 122. The drive ring pushes on all the blocks 122 simultaneously and moves them all axially upwardly in recesses 116 and also radially outwardly as the ribs 150 slide in the channels 118. The blocks 122 are thus driven upwardly and outwardly in unison towards the expanded position shown in FIG. 23.

[0072] The movement of the blocks 122 is eventually limited by contact with the spring retainer 140. When the spring 136 is fully compressed against the retainer 140, it acts as a stop and the blocks can travel no further. There is provision for adjustment of the maximum travel of the blocks 122. This adjustment is carried out at the surface before the tool is put into the borehole. The spring retainer 140 connects to the body 106 via a screwthread at 186. A wrench slot 188 is provided between the upper cap 142 and the spring retainer 140, which provides room for a wrench to be inserted to adjust the position of the screwthreaded spring retainer 140 in the body 106. This allows the maximum expanded diameter of the reamer to be set at the surface. The upper cap 142 is also a screwthreaded component and it is used to lock the spring retainer 140 once it has been positioned.

[0073] The outer part 126 of each cutter block is a steel structure with side face 200 which is the leading which is the leading face in the direction of rotation. An area 204 of this face is slanted back. This steel outer part 126 incorporates cylindrical pockets which receive the cylindrical bodies of cutters of the type shown in FIG. 17. The cutters are held in place by brazing. The front faces 63 and the surrounding surfaces 66 are exposed within the area 204.

[0074] The outward facing surface of the outer block part 126 comprises a part-cylindrical outward facing surface 221 with a radius such that the surface 221 is centred on the tool axis when the cutter blocks are fully extended. The cutter 211 is positioned so that its radially outer edge is at the same distance from the tool axis as the surface 221. There is also a part-cylindrical outward facing surface 222 which is further out from the tool axis and again is centred on the tool axis when the cutter blocks are fully extended. The edge of cutter 212 is at the same distance from the tool axis as the surface 222. This pattern of a cutter and a part-cylindrical outward facing surface where the surface and the radial edge of the cutter are both at the same distance from the tool axis is repeated along the block by cutter 213 and surface 223, cutter 214 and surface 224 and so on at progressively greater radial distances from the tool axis. Transitional surfaces 227 connecting adjacent surfaces 221 and 222, similarly 222 and 223 and so on, have the same curvature as, and are aligned with, the curved edges of cutters 211-216.

[0075] For use as a section mill, the tool is attached to a drill string and lowered into the borehole tubing 68 to the required depth. The drill string is then rotated and the tool is expanded by pumping fluid into flowbore 108 as described above. The radially outer edge of cutter 216 contacts the interior face of the tubing 68 and cuts into it. This allows expansion to continue and the cutters 215 to 211 contact the inside face of the tubing in sequence, cutting into and through the tubing until the fully expanded position of the blocks is reached. The tool is then advanced axially. This is illustrated by FIG. 25 which shows the outer part 126 of a cutter block in use to remove tubing 68 within a borehole. Numeral 107 indicates an edge of the outer wall of the tool body 106, exposed at the side of a recess 116. The tool is now advancing axially in the downward direction shown by arrow D. The leading cutters 211 on each cutter block are positioned to any corrosion or deposits 252 and also remove some material from the inside wall of the tubing 250, thus exposing a new inward facing surface 254.

[0076] The amount of expansion of the tool is arranged such that when the cutter blocks are fully expanded, the surfaces 221 and the outer extremities of the leading cutters 211 are at a radial distance from the tool axis which is slightly greater than the inner radius of the tubing 250 but less than the outer radius of the tubing. If necessary, the amount of expansion is limited by adjusting the screwthreaded spring retainer 140 in the body 106, using a wrench in the wrench slot 188 while the tool as at the surface so that expansion goes no further than required.

[0077] The new internal surface 254 is at a uniform radius which is the radial distance from the tool axis to the extremities of the leading cutters 211. Because the part-cylindrical outward facing surfaces 221 of the three blocks have a curvature which is centred on the tool axis and at the same radial distance from the tool axis as the extremities of the leading cutters 211, they are a close fit to this surface 254 created by the cutters 211, as is shown in FIG. 25, and act as guide surfaces which slide over this new internal surface 254 as the tool rotates. The tool axis is thus positioned relative to the tubing 250.

[0078] As the tool advances axially, the cutters 212 which extend outwardly beyond the surfaces 221 remove the remainder of the tubing indicated at 256 outside the new surface 254 so that the full thickness of the tubing 250 has been removed. The cutters 213 to 216 cut through any cement or other material which was around the outside of the tubing.

[0079] Because the part-cylindrical surface 221 is centred on the tool axis when the cutter blocks are fully expanded, the tool is configured for removing tubing of a specific internal diameter. However, the tool can be used to remove tubing within a range of internal diameters by preparation at the surface, before it is put into a borehole. The tool is configured by fitting the cutter blocks with outer parts 124 dimensioned so that the radius of curvature of the surface 221 is the same as or slightly larger than the original (i.e. as manufactured) internal radius of the tubing to be removed. Also, at the surface, spring retainer 140 is adjusted, using a wrench in slot 188, so that expansion of the tool is limited to the extent required, at which the cutters 211 create the new internal surface on line 254 and the surfaces 221 are a close fit against this surface.

[0080] FIG. 26 is a cross section showing the cutter 211. As can be seen the part of the face 66 close to the inside wall of the tubing is the cutting surface and is at a back rake angle of about 50 degrees. FIG. 27 is an enlarged view of the face of the cutter 211. The cutting surface is an arc of the face 66 of the cutter, approximately between the chain dotted lines.

[0081] It will be appreciated that the embodiments and examples described in detail above can be modified and varied within the scope of the concepts which they exemplify. Proportions may be varied and in particular back raked cutting surfaces may be larger or smaller than shown in the drawings. Features referred to above or shown in individual embodiments above may be used together in any combination as well as those which have been shown and described specifically. More particularly, where features were mentioned above in combinations, details of a feature used in one combination may be used in another combination where the same feature is mentioned. Accordingly, all such modifications are intended to be included within the scope of this disclosure as defined in the following claims.