GB2376484A

GB2376484A - Improvements to steerable downhole tools

Info

Publication number: GB2376484A
Application number: GB0114354A
Authority: GB
Inventors: George Swietlik; Joseph Fitzgerald
Original assignee: Pilot Drilling Control Ltd
Current assignee: Pilot Drilling Control Ltd
Priority date: 2001-06-12
Filing date: 2001-06-12
Publication date: 2002-12-18
Anticipated expiration: 2021-06-12
Also published as: GB2376484B; US7216726B2; GB0114354D0; US20030024742A1

Abstract

A downhole tool comprises a joint and a resilient member 65 which extends through the joint and provides a restoring force which tends to straighten the joint. The joint may comprise a flex coupling [61, figure 12] such as a loose splined connection 62 which allows limited articulation of the joint. The downhole tool may further comprise a first drill string section 63 and a second drill string section 64, the first and second drill string sections 63, 64 being interconnected by the joint, the resilient member 65 being bonded, bolted or otherwise fixed to interior surfaces of the first and second drill string sections 63, 64. The resilient member 5 preferably comprises a fluid tight tube which is sealed to the interior surface of the first and second drill string sections 63, 64. A further downhole tool comprises primary and secondary sleeves 4, 6 which are supported for rotation relative to the mandrel 10 of the drill string, a series of gear wheels 30 being provided to transfer rotational drive from one of the sleeves to the other. The primary sleeve 4 may be a drill string stabiliser and may be mounted on the mandrel 10 eccentrically relative to a rotational axis of the mandrel 10.

Description

1 2376484

IMPROVEMENTS TO STEERABLE DOWNHOLE TOOLS

This invention relates to improvements to steerable downhole tools and particularly, although not 5 exclusively relates to a device for locking and unlocking an asymmetrical offset sleeve relative to a drill string which rotates within it.

It is known to provide a steering device on the lower 10 end of a drill string in order to steer the borehole away from the vertical. In certain circumstances, it is desirable to steer the drill bit in a short radius curve, in order to avoid certain rock structures or to tap into or drain smaller pockets of oil or gas. Many 15 systems have been proposed for short radius curve drilling. One of these utilises a mud rotor to rotate a drill bit. The drill bit is tilted relative to the wellbore centreline, so that it drills a curved path.

The rotational orientation of the motor housing in the 20 borehole determines the direction of the curve of the borehole, so some means must be provided in this system to keep the motor housing oriented while drilling.

An alternative system for short radius curve drilling 2s comprises what is known as a "constrained-rotary" drilling system. This system employs a flexible drive shaft which rotates inside an articulated non-rotating housing. A "curve guide" made of resilient material acts as a spring to apply a side force to the bit and 30 thereby to cause the bit to drill a curved path.

A further system for short radius curve drilling comprises the "rotaryguided" system, in which a flexible drill collar is oriented by specialist 3s downhole equipment. In this system, the flexible joint is provided in the drill string towards it lower end

and the flexible joint is pushed towards one side of the hole to tilt the bit. The pushing force can be provided by a standard mule-shoe sub for gyro orienting and a non-magnetic mule-shoe sub for magnetic 5 orienting. This system is general! y cQn-sid-ered cheaper than the above-described methods. However, there are significant disadvantages in the systems currently available. These are: 10 1. The orientation equipment is not sufficiently stable and can therefore rotate slightly with the drill string thereby causing the borehole to veer off from its desired direction.

15 2. If the orientation equipment loses its grip significantly it can rotate around the bore hole in an uncontrolled fashion, gouging out the sides of the borehole. 20 3. No satisfactory means has been devised for biasing the flexible joint into a straight orientation, so that the assembly does not necessarily return to straight drilling, if the side force on the flexible joint provided by the orientation equipment is removed.

2s The prior systems have relied on rotary seals to seal the interior of the drill string relative to the exterior of the drill string. These rotary seals have caused maintenance and reliability problems and it 30 would be preferably if they could be avoided.

In the prior art devices, means must be provided to

latch and unlatch the orientation equipment relative to the rotating drill string. As the drill string can be 35 rotating at speeds of from lOO to 300 rpm, and as the torque on the drill string as the drill bit advances

can be enormous, reliable direct latching and unlatching of the orientation equipment relative to the drill string is difficult to achieve.

5 The various aspects of the present invention have been developed with these disadvantages in mind.

According to the first aspect of the present invention there is provided a downhole tool comprising a joint 10 and a resilient member which extends through the joint and provides a restoring force which tends to straighten the joint.

Preferably, the joint comprises a flexible joint, and 15 may for example comprise a loose splined connection which allows limited articulation of the joint.

Preferably, the range of articulation is from 1 to 5 degrees from a longitudinal centreline of a downhole tool. Most preferably, the maximum articulation is 3 20 degrees.

Preferably, the downhole tool further comprises a first drill string section and a second drill string section, the first and second drill string sections being 2s interconnected by the joint, the resilient member being bonded, bolted or otherwise fixed to interior surfaces of the first and second drill string sections.

Preferably, the resilient member is tubular.

30 Preferably the resilient member comprises a fluid tight tube which is sealed to the said interior surfaces of the second drill string sections. The resilient member may, for example, be made from an elastomer, plastic material and/or rubber material.

According to a second aspect of the present invention there is provided a downhole tool comprising primary and second sleeves which are supported for rotation relative to the mandrel of the drill string, means 5 being provided to transfer rotational drive from one of the sleeves to the other.

Preferably, the primary sleeve is spaced from and is adjacent to the secondary sleeve in a longitudinal 10 direction of the drill string.

Preferably, the primary sleeve comprises a drill string stabilizer. Preferably, the primary sleeve is or can be made eccentric relative to a rotational axis of the 15 mandrel. For example, the sleeve may be made such that one side of the sleeve projects radially outwardly further than the opposite side of the sleeve.

Alternatively, the sleeve may be provided with a retractable projection which can be forced outwardly to 20 apply pressure to a side of the borehole.

Preferably, the drive means comprises a gear wheel.

Preferably, the gear wheel is mounted on the mandrel, and/or rotates in a plane parallel to a rotational axis 25 of the mandrel, and/or engages respective gears formed around the primary and secondary sleeves.

Preferably, the gear wheel comprises a large gear wheel and a smaller gear wheel, so that there is a gear ratio 30 between the primary sleeve and the secondary sleeve.

Preferably, the gear wheels are superimposed one on top of the other. Preferably, the gear wheels are integrally formed and may be machined from a single piece of metal.

Preferably, the large gear wheel engages only the gear on the secondary sleeve and the small gear wheel engages only the gear on the primary sleeve or vice versa. With this arrangement, rotation of the 5 secondary sleeve in a first direction causes rotation of the primary sleeve in the opposite direction.

Preferably, there are a plurality of gear wheels.

Preferably the gear wheels are equidistantly spaced 10 around the circumference of the mandrel.

Preferably, there are two gear wheels which are mounted on a driveshaft which passes through the mandrel, one of the gear wheels engaging only a gear formed on the 15 primary sleeve and the other gear wheel engaging only a gear formed on the secondary sleeve. Preferably, the gears are of different diameters and/or have a different number and/or size of teeth.

20 Preferably, the gears formed on the primary and secondary sleeves are rings gears which may be formed on the ends of the sleeves which are adjacent one another. 25 Preferably, the driveshaft runs through a tube which extends across the mandrel substantially at right angles to the rotary axis of the mandrel. Open ends of the tube may be sealed to the mandrel, so that the interior surface of the mandrel is sealed from the 30 exterior surface of the mandrel.

Preferably, the primary and second sleeves are each mounted on respective bearings located in or on the outer surface of the mandrel.

Preferably, an annular cover is provided over the gear wheels. The cover may be sealed to the mandrel and/or to one or both sleeves. Preferably, the cover is free to rotate relative to the mandrel and/or relative to 5 one or both sleeves.

Preferably, the outside diameter of the cover is larger than the outside diameter of the secondary sleeve.

Consequently, in operation of the downhole tool, the 10 projecting portion of the primary sleeve engages one side of the borehole and the cover engages the other side of the borehole at a position displaced approximately 180 degrees from the point of engagement of the primary sleeve with the borehole.

In an alternative arrangement, the outside diameter of the secondary sleeve is greater than the outside diameter of the cover (or no cover is provided). In this arrangement the secondary sleeve engages the other 20 side of the borehole at a position displaced approximately 180 degrees from the point of engagement of the primary sleeve with the borehole.

Preferably, means is provided for locking or braking 25 one or both sleeves relative to the mandrel. The said means may comprise a pin which is housed in the mandrel and engages in an opening in the sleeve to lock the sleeve relative to the mandrel. Preferably, at least two pins are provided to lock the sleeve. Preferably, 30 the pins are of different size and/or are spaced apart in a direction parallel to a rotational axis of the mandrel and/or are spaced apart asymmetrically around the circumference of the mandrel.

3s Preferably, the or each pin is driven radially outwardly into engagement with the sleeve by an

actuating mechanism. Alternatively, the or each pin is driven in a direction substantially parallel to the rotational axis of the mandrel by an actuating mechanism. For example, the pin may engage in a recess 5 formed in an end of the sleeve.

The actuating mechanism may be of any suitable type and may, for example, comprise a simple "lock-on/lock-off mechanism which is operated by changes in fluid 10 pressure applied to the actuating mechanism.

Alternatively, the actuating mechanism may comprise a more sophisticated sliding sleeve arrangement comprising a ball assembly which is driven on an endless track between a series of rest positions which 15 define operative states of the device. Preferably, the motive force to cycle the sliding sleeve arrangement is provided by changes in fluid pressure applied to the actuating mechanism. Preferably, the said fluid comprises drilling fluid which may be pumped down the 20 drill string in the interior of the mandrel.

According to a third aspect of the present invention, there is provided a downhole tool comprising a sleeve rotatably mounted on a mandrel of a drill string, means 25 being provided for locking or braking the sleeve relative to the mandrel, the said means comprising a locking member which moves in a direction substantially perpendicular to a radial direction of the mandrel to lock or unlock, brake or release the sleeve. As the 30 locking member moves in a direction which is substantially perpendicular to a radial direction of the mandrel, in the unlocked position, the locking member does not need to project into the mandrel and there is no need to provide a fluid tight seal to the 3s interior of the mandrel.

According to a fourth aspect of the present invention, there is provided a downhole tool comprising a sleeve rotatably mounted on a mandrel of a drill string, and a gear wheel rotatably mounted on the mandrel in a plane 5 substantially parallel to a rotational axis of the mandrel, the gear wheel engaging a ring gear formed on an end of the sleeve, such that rotation of the gear wheel causes rotation of the sleeve and vice versa.

Preferably, the gear wheel is driven to rotate the 10 sleeve a predetermined amount relative to the mandrel.

Alternatively, the gear wheel can provide feedback on the position of the sleeve relative to the borehole.

In a preferred arrangement, the gear wheel is rotated 15 by means of an impeller located within a flow of fluid in the mandrel. Preferably, the impeller is connected to the gear wheel by means of a driveshaft.

According to a fifth aspect of the present invention, 20 there is provided a downhole tool comprising a rotatable mechanism, a mandrel and an impeller rotatably mounted in the mandrel, and means for pumping fluid through the mandrel to rotate the impeller and thereby to operate the rotatable mechanism.

2s According to a sixth aspect of the present invention, there is provided a downhole tool which incorporates a flex joint (for example for directional control, vibration control or to accommodate high bend hole 30 curvatures) wherein within the flexing member there is a resilient flow tube which acts as a spring to restore the systems straightness once the lateral force has been reduced or removed.

According to a seventh aspect of the present invention, there is provided a downhole tool that deploys two sleeves one eccentric with either a fixed or expandable/retractable offset blade or pad and the 5 other concentric. The diameters and or circumferences of each are such that the only part of the eccentric sleeve that makes contact with the formation is the offset blade/pad whilst the portion of the circumference on the concentric sleeve makes contact 10 with the formation at 180 degrees - directly opposite from the offset pad.

According to an eighth aspect of the present invention, there is provided a downhole tool that deploys two 15 sleeves one eccentric with either a fixed or expandable/retractable offset blade or pad and the other concentric. The diameters and or circumferences of each are such that the only part of the eccentric sleeve that makes contact with the formation is the 20 offset blade/pad whilst a portion of the circumference on an Outer Ring mounted on the Idler Wheel makes contact with the formation at 180 degrees - directly opposite - from the offset pad.

25 According to a ninth aspect of the present invention, there is provided a downhole tool that deploys concentric or eccentric sleeves wherein one or the other is mounted above the other up from the drill bit.

30 According to a tenth aspect of the present invention, there is provided a downhole tool that uses two sleeves independently mounted on bearings on a main body mandrel and that can be locked onto the mandrel either

independently or both at the same time via a downhole mechanism. According to an eleventh aspect of the present 5 ln.rention, there is pro Wed a linkage drive s,rstem between two independently mounted sleeves which allows for selective rotational forward or backward drive between the two sleeves or the locking together of the sleeves such that they may rotate in phase and at the 10 same speed as the main mandrel body.

According to a twelfth aspect of the present invention, there is provided a linkage drive system between two independently mounted sleeves which allows for 15 selective rotational forward or backward drive between the two sleeves or the locking together of the sleeves such that one Sleeve may rotate in phase or direction and at the same speed as the main mandrel body.

20 According to a thirteenth aspect of the present invention, there is provided a Linkage Drive between two sleeves that may also be driven by the fluid flow of drilling mud through the centre of the pipe.

25 According to a fourteenth aspect of the present invention, there is provided a downhole tool comprising two sleeves mounted on a main mandrel and a drive linkage which links the sleeves (preferably an offset sleeve and a slave sleeve) to each other in such a way 30 as to cause the slave sleeve to rotate differentially to the rotation of the main body. With this arrangement, if the slave sleeve is braked or locked the offset sleeve repositions itself in orientation when static; i.e. when not being rotated at the same 35 speed and in the same direction as the main body.

Embodiments in accordance with various aspects of the 5 present invention provide a simple tool which could be used as an inexpensive and easy to develop "3-D Point the Bits tool and allows dynamic re-orienting of the sleeve whilst in the de-latched position.

10 The tool can be configured with a rotating/non rotating offset stabiliser sleeve mounted above a torsionally rigid flex joint. The flex joint is preferably calibrated to deflect laterally over a range of angles against known side load values. Within the flex joint 15 is a resilient member which may comprise a tube. If it is configured as a tube, it has a dual purpose by providing: A) A restoring spring force to a straighten the joint 20 to a dead ahead position B) A conduit for the drilling fluid to pass through without leakage.

In a preferred embodiment of the present invention, the 2s tool is made up of the 3 main housing component parts: Lower Flex Joint Mandrel c/w male Drive Coupling Upper Flex Hsng c/w integral female Drive Coupling & Latchable Offset Sleeve 30 Latching Operating Mechanism Housing The main subsidiary parts in each section:

Lower Flex Joint Nut (l) Lower Contact/Off Bottom Ring (2) Lateral Elastomer Ring (3) Smcil' tall 3 nit (d? Seal Carrier (5) Upper Flex Housing Bearing Sleeve (6) 10 Latch Pins & Bushes (7) Lower Contact/On Bottom Ring & Elastomer (8) Spring/Flow Tube (9) Latching Operating Housing 15 Cam Sleeve sub-assembly (lo) Nozzle (ll) Spring (12) Comp. Piston (13) Latch Pin Drive Shaft (14) 20 Bushes (15) In this embodiment the number of component parts is minimized to save cost and reduce complexity. Another issue was to avoid rotary seals and therefore in this 25 embodiment no attempt has been made to provide clockwise and anticlockwise correction control of the sleeve. In one embodiment the sleeve is machined with a fixed 30 offset. The advantage of this over an embodiment with an expanding/retractable pad on the sleeve is its simplicity. The latching and de-latching of the sleeve can be provided through a pumps on - pumps off cycling

process where a closed loop cam either allows the mechanism to fall or remain static when the pumps are switched on. This in turn activates pins to engage or disengage from the sleeve. These pins can either latch 5 from underneath or from the side.

The sleeve may have a magnetic pick up which aligns with a magnetic sensor on the mandrel body when it is locked in the appropriate orientation position to the 10 mandrel body. This ensures accurate and reliable alignment. For a better understanding of the present invention and to show how the same may be carried into effect 15 reference will now be made, by way of example, to the accompanying drawings, in which: Figure 1 is a side view of the cross shaft drive assembly providing drive between two sleeves mounted on 20 a drill string mandrel; Figure 2 is a cross-section on the line A-A in Figure 1; 25 Figure 3 is a cross-section on the line B-B in Figure 1; Figure 4 is a view of the other side of the cross shaft drive assembly; Figure 5 is a perspective view of the cross shaft drive assembly;

Figure 6 is a side view of an idler gear drive assembly providing drive between two sleeves mounted on a drill string mandrel; 5 Figure 7 'S a cross-section on the line 7 - of Figure 6; Figure 8 is a perspective view of an enclosed drive assembly providing drive between two sleeves mounted on 10 a drill string mandrel; Figure 9 is a side view of the drive assembly of Figure 8; 15 Figure 10 is a cross-section on the line B-B in Figure 9; Figure 11 is a perspective view of a locking mechanism which is operable to prevent relative rotation between 20 a sleeve and a mandrel; Figure 12 is a side view of the locking mechanism of Figure 11; 25 Figure 13 is a cross-section on the line A-A in Figure 12; Figure 14 is a view on an end of the offset sleeve illustrated in Figure 12; Figure 15 is a cross-section on the line B-B of Figure 14;

Figure 16 shows an alternative embodiment of locking arrangement for a sleeve attached to the mandrel of a drill string; S Figure 17 is a side view of the locking arrangement of Figure 16; Figure 18 is a crosssection on the line C-C of Figure 17; Figure 19 is a perspective view of an alternative drive arrangement for controlling the relative rotation between a sleeve and the mandrel of a drill string; 15 Figure 20 is a cross-section on the line A-A of Figure 19; Figure 21 is a cross-section on the line A-A of Figure 20; and Figure 22 is a cross-section on the line B-B of Figure 20. Figures 1 to 5 show a cross shaft drive assembly 2 25 comprising an offset sleeve 4 and a slave sleeve 6 which are mounted on bearings 8 on a mandrel 10 of a drill string. The slave sleeve 6 is concentric relative to a rotational axis X-X of the drill string, whereas the offset sleeve 4 is not concentric and is 30 provided with a raised portion 12 which extends radially outwardly from the rotational axis X-X of the drill string further than the remainder of the offset sleeve 4.

A pair of idler gear wheels 14, 16 provide a rotational interconnection between the offset sleeve 4 and slave sleeve 6. The idler gear wheels 14, 16 are rigidly 5 interc^rAne tGd bait - =zns of a cross shaft 18 located i n a cross shaft tube 20 which extends through a central region of the mandrel 10 in a direction parallel to the rotational axis X-X of the drill string.

lo The larger idler gear wheel 14 engages a ring gear 22 formed on the end of the offset sleeve 4 adjacent the slave sleeve 6, whereas the smaller idler gear wheel 16 on the opposite side of the mandrel 10 engages a smaller ring gear 24 formed on the end of the slave 15 sleeve 6 adjacent the offset sleeve 4.

In an offset drilling operation, the mandrel 10 rotates at a speed of approximately 100 to 300 rpm and the offset sleeve 4 and slave sleeve 6 remain stationary 20 with the mandrel 10 rotating within them. It will be appreciated that the offset sleeve 4 and slave sleeve 6 are a tight fit within the borehole, but because of the offset of the sleeve 4, there is only point contact with the borehole. This point contact occurs at the 25 raised portion 12 of the offset sleeve 4, and on the portion of the slave sleeve 6 which is disposed 180 degrees around from the raised portion 12 of the offset sleeve 4. As a consequence of this point contact, the mandrel 10 is not concentric with the borehole.

If the cross shaft drive assembly forms part of a downhole tool comprising a drill bit with a flex coupling, the offsetting of the mandrel 10 in relation

to the borehole causes the drill bit to drill a curved hole. If the direction of drilling is to be altered, it is necessary to rotate the offset sleeve 4, so that the raised portion 12 engages the borehole at a s different rotational position. In this embodiment, rotation of the offset sleeve 4 is achieved by braking or locking the slave sleeve 6 relative to the mandrel 10. This can be achieved by applying a brake shoe or other braking device to the inside surface of the slave lO sleeve 6 or by forcing a pin in the mandrel 10 into the slave sleeve 6. Various mechanisms for achieving this are discussed later.

With the slave sleeve 6 braked or locked to the mandrel 15 10, the slave sleeve 6 rotates with the mandrel 10, and by engagement of the ring gear 24 with the small idler gear wheel 16, the cross shaft 18 is caused to rotate and thereby to drive the larger idler gear wheel 14 to rotate. This in turn causes rotation of the offset 20 sleeve 4, by engagement of the ring gear 22 with the larger idler gear wheel 14. In this embodiment, the offset sleeve 4 is caused to rotate in the same direction as the slave sleeve 6 and the mandrel 10, but because of the difference in size between the larger 25 idler gear wheel 14 compared to the smaller idler gear wheel 16, there is a gear ratio between the offset sleeve 4 and the slave sleeve 6, so that the offset sleeve 4 turns faster than the slave sleeve 6. Of course any combination of sizes of the idler gear 30 wheels can be selected to provide any desired gear ratio between the offset sleeve 4 and slave sleeve 6.

Once the raised portion 12 of the offset sleeve 4 has been rotated into the correct position, the slave sleeve 6 can be unbraked or unlocked, so that the slave sleeve 6 and offset sleeve 4 again come to rest in the 5 borehole.

Figures 6 and 7 show an alternative embodiment of sleeve drive assembly in which the idler gears are not rigidly connected together. In this and later 10 embodiments, the same reference numerals have been used as in the previous embodiment for the corresponding components, and the operation of the assembly is identical to the previous embodiment except where stated otherwise.

Four idler gear wheels 30 comprising a large gear 32 integrally machined with a smaller gear 34 are equidistantly spaced around the mandrel 10 on a collar 35. The collar 35 is mounted by means of bearings 36 20 on the mandrel 10, so it is free to rotate about the mandrel 10 and each idler gear wheel 30 is mounted by means of bearings 37 on the collar 35. The larger gears 32 of each idler gear wheel 30 engage with a ring gear 38 formed on an end of a slave sleeve 6 which is 25 adjacent an offset sleeve 4. Similarly, the smaller gears 34 of each idler gear wheel 30 engage a ring gear 40 formed on an end of the offset sleeve 4 adjacent the slave sleeve 6.

30 As in the previous embodiment, in normal operation, the mandrel 10 is rotating and the slave sleeve 6 and offset sleeve 4 are stationary in the borehole. It is necessary to rotate the offset sleeve 4, so that the

raised portion 12 of the offset sleeve 4 is rotated relative to the borehole, in order to change the direction of drilling. This is achieved by locking the slave sleeve 6 with the mandrel 10, so that the slave 5 sleeve 6 turns with the mandrel 10. This causes the idler wheels 30 to rotate by engagement of the large gear wheels 32 of the idler gear wheels 30 with the ring gear 38. Consequently, the offset sleeve 4 is caused to rotate by engagement of the ring gear 40 with 10 the small gear wheels 34 of each idler gear wheel 30.

In this embodiment, the offset sleeve 4 is driven to rotate in a direction opposite to the direction of the slave sleeve 6 and there is a gearing effect caused by the difference in size of the large gear wheels 32 15 compared to the small gear wheels 34 of each idler gear wheel 30, such that the offset sleeve 4 rotates slower than the slave sleeve 6.

Figure 8 shows an alternative embodiment of sleeve 20 drive assembly which is identical to the last embodiment, apart from the inclusion of a cover 42 which fits over and encloses the idler gear wheels 30.

In a preferred embodiment, the outside diameter of the 25 cover 42 is larger than the outside diameter of the slave sleeve 6, so the cover 42 engages the borehole rather than the slave sleeve 6.

Although the above embodiments describe the use of four 30 idler gear wheels 30, each comprising a large gear wheel 32 integrally formed with a smaller gear wheel 34, any number of idler gear wheels 30 is contemplated.

Indeed, in certain applications only a single idler

gear wheel 30 would be adequate. Furthermore, each idler gear wheel 30 could comprise a single gear or gears of any combination of sizes integrally formed or otherwise connected together. Also the gears could be 5 bevel gears or could comprise friction drive elements without gear teeth.

In the above embodiments, there is a description of how

the slave sleeve 6 may be braked or locked relative to lo the mandrel 10. It is also contemplated that the offset sleeve 4 may be braked or locked directly to the mandrel 10. Referring to Figures 12 to 15, locking of either the slave sleeve 6 or the offset sleeve 4 is provided a lock pin 50 located in a recess 52 formed in 15 the mandrel 10, and movable from an unlocked position into a locked position (as illustrated in Figure 11) in a direction parallel to the rotational axis X-X of the mandrel 10. In the locked position, the pin 50 engages a corresponding recess 54 formed in the offset sleeve 20 4. As best shown in Figure 15, the pin 50 is forced from the unlocked to the locked position by means of any appropriate downhole actuating mechanism, such as a simple "push-on push- off piston arrangement 56. This piston arrangement 56 is moved against the action of a 2s return spring 58 by means of changes in fluid pressure within the hollow interior 50 of the mandrel 10. Figures 12 and 15 also illustrate the construction of a flex coupling 61,

referred to above. The flex coupling 30 61 comprises a loose splined connection 62 between an upstream portion 63 and a downstream portion 64 of the mandrel 10, and provides 1 to 5 degrees, and preferably 3 degrees, of lateral movement or "wobble" from the

rotational axis X-X of the upstream portion 63 of the mandrel lO.

The splined connection 62 is sealed by a "top hat" 5 shaped tubular resilient element 65 which is connected by means of fluid tight seals 66, 67 to the upstream portion 63 and downstream portion 64 of the mandrel lO.

The resilient element 65 may be made, for example, from an elastomer, from natural rubber or from a plastics 10 material.

In addition to or instead of providing a fluid tight seal to the splined connection 62, the resilient element 65 biases the flex coupling into alignment with 15 the rotational axis X-X of the upstream portion 63 of the mandrel lo. This resilient biasing could be provided by other shapes of resilient element, such as a solid cylindrical element.

20 Figures 16, 17 and 18 illustrate an alternative arrangement in which a "push-on push-off" downhole mechanism is operable to force pins 70, 72 into corresponding openings 74, 76 in an offset sleeve 4.

In order to facilitate the movement of the pins 70, 72 25 in a direction substantially parallel to the rotation axis X-X of the mandrel lO, the pins 70, 72 may be mounted in bushes or bearings (not shown) housed in the mandrel lo.

30 The actuating mechanism comprises a piston 82 which is driven along the rotational axis X-X of the mandrel lO in a downhole or uphole direction against a return spring 84 by changes of internal fluid pressure within

the hollow interior 86 of the mandrel lo. Recesses 88, 90 are formed in opposite sides of the piston 82 and act as camming surfaces on which the pins 70, 72 ride.

When the piston 82 is positioned such that the recesses 88, 90 are aligned with the pins 70, 72, the pins are forced under the action of springs 92/ 94 to drop down into the recesses 88, 90 and thereby are retracted from the openings 74, 76 formed in the offset sleeve 4.

In an unlocked configuration, the offset sleeve 4 comes to rest in the borehole and the mandrel lO is free to rotate in it. If however a pulse of fluid pressure is applied within the mandrel lo to the piston 82, the 15 piston is driven along the rotational axis X-X of the mandrel lo. As this occurs, the inner ends of the pins 70, 72 ride up the edges of the recesses 88,90 and are driven into the openings 74, 76 formed in the offset sleeve 4. This causes the offset sleeve 4 to be locked 20 relative to the mandrel lo and therefore to rotate with it. It will be appreciated that by again changing the internal fluid pressure in the mandrel lo, the piston 82 will be moved back along the rotational axis X-X of the mandrel lO such that the recesses 88, 90 again 25 align with the pins 70, 72, so that the pins drop back out of the holes to release the offset sleeve 4.

In this embodiment, two pins 70, 72 are used. However, any number and combination of pins is contemplated.

It will be appreciated that if two pins are used and the pins are spaces 180 degrees apart, it is possible for the pins to align in two positions in a 360 degree

rotation of the offset sleeve 4 relative to the mandrel 10. Consequently, in the absence of any other indication, it would not be possible to ensure that the offset sleeve 4 had been locked in the correct position 5 relative to the mandrel 10 and hence that the angle of drilling was correct. This problem is addressed in this embodiment by offsetting the pins and using pins of different diameters so that the pins can only align in one position in a 360 degree rotation of the offset 10 sleeve 4 relative to the mandrel 10. In an alternative embodiment, not illustrated, in addition or instead of offsetting the pins or using pins of different diameters, the pins can be staggered, such that they are asymmetrically disposed about the rotational axis 15 X-X of the mandrel 10. This again only allows alignment in one relative position between the offset sleeve 4 and the mandrel 10.

The locking arrangements described above in relation to 20 direct locking of an offset sleeve can also be used to lock a slave sleeve as described in the earlier embodiments. Furthermore, the mechanisms which have been described to force pins in and out of engagement with the offset sleeve could be used to apply a brake 25 pad to an end or the underside of the offset sleeve, thereby to slow it down or bring it to rest. The braking elements could comprise conventional friction elements having substantially the form of an automotive brake shoe, but adapted for downhole use.

Figures 19 to 22 illustrate a further embodiment in which an offset sleeve 4 is rotated by means of an impeller 100. The impeller 100 is rotatable mounted on

a drive shaft 102 which extends across the mandrel 10 in a direction perpendicular to the rotational axis X-X of the mandrel 10. The drive shaft 102 is mounted in bearings or bushes (not shown), extends through the mandrel 1 O at one end and is fixed to a gear wheel 104. A ring gear 106 formed on the end of the offset sleeve 4 adjacent the gear wheel 104 meshes with the gear wheel 104, so that drive from the impeller 100 is transferred through the gear wheel 104 to the offset 10 sleeve 4.

In the course of normal drilling operations, drilling fluid is pumped through the hollow interior 108 of the mandrel 10 towards the drill bit (not shown) in the 15 direction of the arrow F in Figure 21. In the illustrated embodiment, the hollow interior 108 of the mandrel 10 is reduced gradually in diameter to form a venturi 110 which directs the drilling fluid onto vanes 112 of the impeller 100. As the drilling fluid is 20 forced through the venturi 110, its velocity increases, so that as the drilling fluid impinges on the vanes 112, it creates a considerable torque, tending to rotate the drive shaft 102, the gear wheel 104 and offset sleeve 4.

If the offset sleeve is employed in directional drilling, a braking or locking arrangement, as described in the previous embodiments may be employed, to brake or lock the offset sleeve 4. A brake 30 arrangement 114 is shown schematically in Figure 21.

An actuating mechanism, such as is described in the previous embodiment, can be used to selectively push the braking mechanism 114 into engagement with an

underside of the offset sleeve 4, thereby to brake the sleeve relative to the mandrel l0.

The impeller 100 of this embodiment is used to rotate 5 an offset sleeve 4, but it could be used to drive any downhole tool such as a drill bit or hydraulic pump.

In addition, instead of being driven by the drilling fluid, the impeller 100 could be driven by a separate hydraulic source, for example located at the head of 10 the borehole. Finally the impeller of the previous embodiment could be replaced with an electric or hydraulic motor.

1) CROSS SOFT LINKAGE DRIP

15 li)List of Reference Numbers 6) Bearing Mounted Slave Sleeve. This can be fluted with either straight or left-handed spiral.

30) Idler Wheels 20 18) Cross Shaft 20) Cross-shaft Tube 4) Bearing Mounted Offset Sleeve. This can have a larger and or wider offset blade to the other blades on the tool.

25 lo) Main Body Mandrel 61) The flexible housing body. With a through tube to aid as a restoring force.

56) Operating Mechanism (not shown) to act onto one or the other of the sleeves either a friction/braking 30 force or locking force or allow complete freedom of movement.

lit) Special Features of the Cross Shaft Linkage Drive There are two idler wheels/gears assembled and Acted.ri cross-shaft. The cross shaft runs at right angles to the rotating axis of the mandrel body.

The shaft is mounted through a static tube and therefore does not require a rotating seal. The Idler wheels are mounted directly onto the body of the 10 mandrel 180 degree apart and between both the slave sleeve and the offset sleeve. Each wheel is only connected to one of the sleeves. The two idler wheels can be of different sizes so as to cause a gearing advantage between the two sleeves and/or mechanical 15 advantage in drive between the two sleeves. The operating mechanism can be designed to interfere with either sleeve thereby resulting in the other sleeve being driven in the opposite direction. Another feature of the design is the incorporation of a conventional 20 one-way drive coupling between the cross-shaft and one of the idler wheels to override backward drive.

Within this concept the Slave Sleeve although concentrically mounted can be made to always makes 25 contact with the formation at 180 deg or directly opposite from the Offset Blade on the front Sleeve. To ensure this the Offset blade on the eccentric sleeve could deploy an expandable shoe/pad whilst in the oriented /static position.

2) SEPARATE BEARING COLLAR MOUNTED DRIVE

2i) List of Reference Numbers 6 Bearing Mounted Slave Sleeve. This can be fluted 5 with either straight or left-handed spiral.

30 Idler Wheels/Gears 35 Bearing Collar for mounting the Idler Wheels 4 Bearing Mounted Offset Sleeve. This can have a larger and or wider offset blade to the other 10 blades on the tool.

10 Main Body Mandrel 61 The flexible housing body. With a through tube to aid as a restoring force.

82 Operating Mechanism (not shown) to act onto one or 15 the other of the sleeves either a friction/braking force or locking force or allow complete freedom of movement 2ii) Special Features of the Cross shaft Linkage Drive 20 The centres of the Idler Wheels/Gears are not forced to rotate circumferentially at the same speed as the main body mandrel. The Idler Wheel/Gear is independently mounted. In this case the drive between the two sleeves can be shared between two or more Idler Wheels/Gears 2s mounted on a collar that is free to rotate independently of both the sleeves and the main body mandrel. Also in this case each Idler Wheel/Gear is in contact with both sleeves at the same time. However a gear reduction could be introduced on the same Idler 30 Wheel to differentiate the drive. Within this concept the Slave Sleeve although concentrically mounted can be made to always makes contact with the formation at 180 deg or directly opposite from the Offset Blade on the

front Sleeve. Or, alternatively, the Idler Wheel/Gear Collar assembly is fitted with an Outer Ring whose Outside Diameter makes contact with the formation at 180 degrees from the Offset Blade/Pad instead of the 5 Slave Sleeve. To ensure this the Offset blade on the eccentric sleeve could deploy an expandable shoe/pad whilst in the oriented /static position. In either case a force is applied from inside the tool to change the relative motion of the Slave Sleeve to the Rotation of 10 the Mandrel Body.

Each of the elements: Slave Sleeve, Collar Mounted Idlers and the Offset 15 Sleeve may be controlled via: A braking force or a locking force back through the mandrel body or left free to attain a steady state. One of the bearings may be designed to have less frictional 20 effects than the other two.

Claims

l. A downhole tool comprising a joint and a resilient member which extends through the joint and 5 provides a restoring force which tends to straighten the joint.
2. A downhole tool as claimed in claim l, in which the joint is a flexible and allows limited 10 articulation.
3. A downhole tool as claimed in claim l or 2, in which the joint comprises a loose splined connection.
4. A downhole tool as claimed in any one of the preceding claims, in which the range of articulation of the joint is from l to 5 degrees from a longitudinal centreline of the downhole tool.
5. A downhole tool as claimed in any one of the preceding claims, in which the range of articulation of the joint is less than or equal to 3 degrees from a : longitudinal centreline of the downhole tool.
6. A downhole tool as claimed in any one of the preceding claims, further comprising a first drill string section and a second drill string section, the first and second drill string sections being 30 interconnected by the joint, the resilient member passing through or being sealed to the first and second drill string sections.
7. A downhole tool as claimed in any one of the preceding claims, in which the resilient member is tubular. 5
8. A downhole tool as claimed in claim 7, in which the resilient member comprises a fluid tight tube which is sealed to interior surfaces of the first and second drill string sections.

lo
9. A downhole tool comprising primary and secondary sleeves which are supported for rotation relative to the mandrel of a drill string, means being provided to transfer rotational drive from one of the sleeves to the other.
10. A downhole tool as claimed in claim 9, in which the primary sleeve is spaced from and is adjacent to the secondary sleeve in a longitudinal direction of the drill string.
11. A downhole tool as claimed in claim 9 or 10, in which the primary sleeve comprises a drill string stabilizer. -i 25
12. A downhole tool as claimed in any one of claims 9 to 11, in which the primary sleeve is mounted eccentrically relatively to a rotational axis of the drill string.

30
13. A downhole tool as claimed in claim 12, in which one side of the sleeve projects radially outwardly further than the opposite side of the sleeve.
14. A downhole tool as claimed in claim 9, in which a retractable projection is provided on the primary sleeve, which projection can be forced outwardly to apply pressure to a side of a bore hole.
15. A downhole tool as claimed in any one of claims 9 to 14, in which the drive means comprises a gear wheel.

10
16. A downhole tool as claimed in claim 15, in which the gear wheel is mounted on the mandrel and/or rotates in a plane parallel to a rotational axis of the mandrel, and/or engages respective gears formed around the primary and secondary sleeves.
17. A downhole tool as claimed in claim 16, in which the gear wheel comprises a large gear wheel and a smaller gear wheel, so that there is a gear ratio between the primary sleeve and the secondary sleeve.
18. A downhole tool as claimed in claim 17, in which the gear wheels are superimposed one on top of the other.

25
19. A downhole tool as claimed in claim 18, in which the gear wheels are integrally formed.
20. A downhole tool as claimed in claim 18 or 19, in which the large gear wheel engages only the gear of 30 the secondary sleeve and the small gear wheel engages only the gear on the primary sleeve or vice versa.
21. A downhole tool as claimed in any one of claims 17 to 20, in which a plurality of gear wheels are provided, the gear wheels being equidistantly spaced around the circumference of the mandrel.
22. A downhole tool as claimed in claim 9, in which the drive means comprises two gear wheels mounted on a drive shaft which passes through the mandrel, one of the gear wheels engaging only a gear formed on the 10 primary sleeve and the other gear wheel engaging only a gear formed on the secondary sleeve.
23. A downhole tool as claimed in claim 22, in which the gears are of different diameters and/or have 15 a different number and/or size of teeth.
24. A downhole tool as claimed in claim 22, in which the drive shaft runs through a tube which extends across the mandrel substantially at right angles to the 20 rotary axis of the mandrel.
25. A downhole tool as claimed in claim 24, in which open ends of the tube are sealed to the mandrel, so that the interior of the mandrel is sealed from the 25 interior of the tube.
26. A downhole tool as claimed in any one of claims 9 to 25, in which the primary and secondary sleeves are each mounted on respective bearings located 30 in or on the outer surface of the mandrel.
27. A downhole tool as claimed in any one of claims 15 to 2G, in which an annular cover is provided

over the gear wheel or gear wheels, the cover being free to rotate relative to the mandrel and/or relative to one or both sleeves.

5
28. A downhole tool as claimed claim 27, in which the outside diameter of the secondary sleeve is greater than the outside diameter of the cover.
29. A downhole tool as claimed in any one of 10 claims 9 to 28, in which means are provided for locking or braking one or both sleeves relative to the mandrel.
30. A downhole tool as claimed in claim 29, in which the said means comprises a pin which is housed in 15 the mandrel and engages in an opening in the sleeve to lock the sleeve relative to the mandrel.
31. A downhole tool as claimed in claim 30, in which there are a plurality of pins, the pins being of 20 different size and/or spaced apart in a direction parallel to a rotational axis of the mandrel and/or spaced apart asymmetrically around the circumference of the mandrel.

2s
32. A downhole tool as claimed in claim 30 or 31, in which the or each pin is driven radially outwardly into engagement with the sleeve by an actuating mechanism. 30
33. A downhole tool as claimed in claim 32, in which the or each pin is driven in a direction substantially parallel to the rotational axis of the mandrel by the actuating mechanism.
34. A downhole tool as claimed in claim 32 or 33, in which the actuating mechanism is operated by changes in fluid pressure applied to the bore hole.
35. A downhole tool as claimed in claim 32 or 33, in which the actuating mechanism is operated by an impeller located within a flow of fluid within the mandrel.