GB2345510A - Bottomhole drilling assembly having a pressure modulation valve assembly - Google Patents

Abstract

A bottomhole drilling assembly comprises a drillstring pressure modulation valve assembly having a spring 22 which bears against a compensation piston 76 at one end and on the other end against a modulating ram needle 27. The pressure modulation valve assembly (A, figure Ib) is situated between a pressure responsive thruster (34, figure 1a) and a fluid-operated drilling motor (50, figure 1c) attached to a drill bit (40, figure 1c). The thruster is responsive to internal pressure differences between itself and the annulus. The thruster acts by telescoping to add to the weight on bit (WOE) thus advancing drilling. Changes in conditions during drilling cause a pressure drop to occur through the drilling motor which increases pressure in the thruster . This causes positive feedback which advances the drill further and may stall the bit or motor. The modulation valve compensates for such changes to minimise the effect of such changes on the operation of the thruster. Piston 76 can be preloaded, with fluid flowing, before drilling commences. Spring-loaded needle 27 reacts to any pressure changes by varying the pressure difference at orifice 31.

Description

PRESSURE MODULATION VALVE ASSEMBLY The field of this invention relates to drilling string pressure modulation valves, particularly those useful in combination with a drill string thruster used in conjunction with a drilling motor during drilling.

One way drilling a borehole can be accomplished is by circulation of fluid through a downhole motor which is operably connected to the drill bit. Such bottom hole assemblies have, at times in the past employed thrusters in an effort to improve drilling efficiency. The thruster is a telescoping tube arrangement which allows the drill bit to advance while the tubing string is supported in a rather stationary position at the surface. Ultimately, when the thruster has advanced its full stroke, or a notable portion thereof, the drill sting is lowered from the surface which causes the upper end of the thuster to slide down and therein close the thruster for the next stroke. When the drilling Kelley or the stand being drilled down by the top drive reaches the drill rig floor, circulation is interrupted and another piece of tubing is added to the string at the surface or the coiled tubing is further unspooled into the wellbore. This also causes the thruster to retract as a result of this procedure and the drilling procedure using the downhole motor begins once again.

In the past, depending on drilling conditions, fluid resistance in the downhole motor varies as a result of torque generated at the drill bit which is connected to the drilling motor. Fluctuations of pressure drop through the motor caused by the above noted bit torque change has in the past impeded the function of the thruster. What had occurred in the past was that the thruster responded to changes in pressure drop through the downhole motor instead of simply feeding out pipe as the drill bit advanced at at a constant weight on bit (WOB). The inability of the thruster to sense relatively constant pressures, regardless of the amount of work the drilling motor was required to do, caused instability to such thrusters to the point of negating their functional operation and negatively impacting the drilling operation.

What occurred was a pressure increase due to higher torque load on the motor as a result of changing drilling conditions. The higher or increased pressure was sensed at the thruster causing it to extend the telescoping portion out further which in turn increased the weight on the bit. Ultimately, with increasing weight on bit the motor torque was greater and the pressure sensed by the thruster was therein greater and drilling would cease as the thruster drove the motor in a stall condition where the drill bit is no longer turning.

In these past applications of the thruster, the weight on bit was a function of the pressure difference between inside and outside the thruster. The greater the difference the more force on the bit is exerted by the thruster. As a result, assemblies using thrusters with downhole motors in combination with drill bits have not been as efficient and useful as possible.

According to a preferred embodiment of the present invention there is provided a pressure modulation valve in the bottom-hole assembly between the thruster and the downhole motor to compensate for pressure increases as a result of changing drilling conditions which have in the past caused an increase in torque and as a result winched the WOB applied by the thruster. Ultimately, it is desired to make a thruster operable when used in conjunction with the drilling motor so that it can efficiently and reliably, without undue cycling or oscillation, feed out pipe in response to advancement of the drill bit during the drilling operation-Use of the pressure modulation valve facilitates a constant weight on the bit since variations in pressure drop in the circulating mud in the drilling motor do not affect the relative force exerted on the bit.

With the modulation feature fully effective, these variations in pressure drop are compensated by the pressure modulation valve with the result being a facilitation of a constant weight on bit regardless of motor differential pressure.

A drill string pressure modulation valve is disclosed which is usable in combination with a downhole drilling motor and a drill string thruster to compensate for changes in pressure drop through the drilling motor which normally occur during drilling. When conditions change during drilling, which in turn changes the pressure drop through the drilling motor, the drill string pressure modulation valve compensates for such changes to minimize the effect of such changes on the operation of the thruster and the resulting WOB created by the thruster. The modulation valve has a feature which allows it to find automatically a balanced preload condition for the main needle valve, the primary functional element within the modulation valve each time the rig pumps are turned off and then turned on.

The modulation valve is fully self-contained, and is assembled as part of the bottom hole assembly. The device senses the no-load pressure drop in the system and sets itself each time the rig pumps are tumed on to compensate for any change in the no-load pressure drop experienced below the device which could be attributable to such things as motor wear, bit nozzle plugging, or changes in the flow rate Accordingly, the hydraulic thrusting force remains constant over a wide range of drilling environments. As the drilling conditions change and the pressure drop in the downhole motor increases, the needle valve shifts to compensate for such additional pressure drop with a resultant small or no effect on the thruster and the resulting WOB created by the thuster located upstream of this modulation value.

Various embodiments of the present invention will now be described, by way of example only, and with reference to the accompanying drawings in : Figure 1A-C illustrates a bottom-hole assembly in a sectional, elevation view showing the layout of the components, as well as a possible location for a measurement while drilling system which can be used in tandem with the apparatus.

Figure 2A-B is a sectional view of the drill string pressure modulation valve in the run-in position without the rig pump circulating.

Figure 3A-B is the view of Figure 2A-B with the pumps circulating, but the bit off bottom.

Figure 4A-B is the view of Figure 3A-B with the pumps running and the drill bit on bottom.

The drill string modulation valve of the present invention is iilustrated in the bottom-hote assembly illustrated in Figure 1A-C. A drill or tubing string 32, which can be rigid jointed pipe, reeled pipe or coiled tubing, supports a drill string thruster 34 and related bottom hole assembly elements. The thruster 34 has an outer housing 36 and an internal pipe 38. The internal pipe 38 is reciprocally mounted within the outer housing 36 and extends as the drill bit 40 advances. The thruster 34 is responsive to pressure difference between internally of the bottom-hole assembly, referred to as 42, and externally in an annulus around the assembly, referred to as 44. The apparatus A is connected to the intemal pipe 38. Below the apparatus A, a measurement while drilling system can be inserted to supply data to the surface regarding formation conditions and/or the rotary orientation of the drift motor assembly 40. The bottom-hole assembly of Figure 1A-C also indicates an upper stabilizer 46 and a lower stabilizer 48 between which is a drilling motor 50.

Optionally, to assist in drilling deviated wellbores, bent subs 52 and 54 can be employed in the bottom-hole assembly as well as, or alternatively, other desirable steering arrangements may be used.

This type of a bottom-hole assembly is typically used for deviated wellbores.

The drilling motor 50 can be a progressive cavity type of a motor which is actuated by circulation from the surface through the drill string 32. The weight or force on the drill bit 40 is determined by the pressure difference intemally to the thruster 34 at point 42 and the annular pressure outside at point 44. The drilling motor 50 is a variable resistance in this circuit in that the pressure drop across it is variable depending on the load imposed on the motor 50 by troque created at the drill bit 40.

For example, as drilling begins, the bit 40 causes an increase in load on the drilling motor 50 which increases the pressure drop between the drilling motor 50 and the annulus 44. That increase in pressure drop raises the pressure difference across the thruster 34 (if the apparatus A is not used) by raising the pressure at point 42 with respect to the pressure at point 44. As a result, the thruster 34 adds an incremental force through the drilling motor 50 down to bit 40. As additional weight is put on the bit 40, the drilling motor 50 increasingly bogs down to the point where this cycle continues until the drill bit 40 stalls the motor 50 due to the extreme downward pressure that is brought to bear on the bit 40 from the ever increasing internal pressure at point 42 inside the thruster 34. The thruster 34 instead of feeding out the internal pipe 38 in direct compensation for the advancement of the bit 40 instead is urged by the rise in pressure intemally at point 42 to feed out the internal pipe 38 at a greater rate than the advancement of the bit 40, thus adding the force on bit, which in turn finally stalls the drilling motor 50. This had been the problem and the apparatus A of the present invention, when inserted in the bottomhole assembly, as shown in Figure 1 B, addresses this problem. The apparatus A acts as a compensation device, which, as its objective, keeps the pressure constant as possible at the internal point 42 of the thruster 34 despite variations in pressure drop that the drilling motor 50 created during drilling.

Referring now to Figure 2A and B, the apparatus A has a containment sub 1 which has a lower end 56 which is oriented toward the drilling motor 50, and an upper end 58, which is oriente toward the thruster 34. In order to describe the operation of the apparatus, the pressure adjacent lower end 56 will be referred to as Pi ; the pressure adjacent the upper end will be referred to as P2 ; and the annulus pressure outside the containment sub 1 will be referred to as P3. Again, the objective is to keep P2 as constant as possible.

The assembly shown in Figure 2 starts near the upper end with lifting head 2 which is supported from the containment sub 1 at thread 60. Attached to the lower end of the lifting head 2 is compressive pad 4, which in turn is secured to a porous metal filter 7. Below the porous metal filter 7, liquid that gets through it flows through mud flow port 6 to a cavity 62 above delay valve piston 9. Delay valve piston 9 is sealed at its periphery by seat 64 to divide the delay valve tube 8 into cavity 62 and cavity 66. Delay valve spring 10 resides in cavity 66 and biases the delay valve piston 9 toward the porous metal filter 7. A delay valve orifice assembly 12 is located at the lower end of the delay valve tube 8. This is an orifice which, in essence, regulates the displacement of clean fluid in cavity 66 into cavity 68. Those skilled in the art will appreciate that movement of delay valve piston 9 downhole toward the lower end 56 will result in displacement of clean fluid, generally an oil, from cavity 66 through delay valve orifice block 11 into cavity 68 for ultimate displacement of piston valve 15. Piston valve 15 is sealed internally in delay valve tube 8 by seal 70. The piston valve 15 has a receptacle 72, which includes a seal 74, which ultimately straddles the low-pressure transfer tube 16, as shown by comparing Figure 2A to Figure 3A. The low pressure transfer tube 16 extends to compensation tube body 20. Inside of compensation tube body 20 is compensation spring 22. Spring 22 bears on compensation piston 76 at one end and on the other end against modulating ram needle 27. Needle 27 is sealed internally in the compensation tube body 20 by seal 78. The compensating piston 76 is also sealed within the compensation tube body 20 by seal 80 Both the compensating piston 76 and the needle 27 are movable within the compensating tube body 20 for reasons which will be described below. In effect, the piston 76 and the needle 27 define a cavity 82 within the compensation tube body 20. The low pressure transfer tube 16 spans the entire cavity 82, but is not in fluid communication with that cavity A vent port 23 is in fluid communication with cavity 82. The port 23 is in fluid communication with cartridge vent port 24, which ultimately leads to transfer groove 25, which in turn leads to the porous metal filter 26. Accordingly, the pressure Pa is communicated into the cavity 82. Port 24 can be sized to make cavity 82 operate as a dampener on the movements of needle 27. It can be directly connected to P3 as shown or to an external or internal reservoir. The reservoir can have a floating piston with one side exposed to P3 through the filter 26. This layout can reduce potential plugging problems in filter 26.

Referring now toward the lower end of the compensation tube body 20, the needle 27 extends beyond an opening 84 and into the restrictor orifice 31. The preferred components for the needle 27 and the restrictor orifice 31 is a carbide material. As illustrated in Figure 2B, the pressure at the inlet of the drilling motor 50 (see Figure 1B) is the pressure Pi, which is also illustrated in Figure 2B. Normal flow to the motor 50 occurs from upper end 58 through passage 86 down around needle 27 and out lower end 56.

In the position shown in Figure 2A, the low pressure transfer tube 16 communicates with cavity 88, which in turn through openings or ports 17 communicates with cavity 90. Those skilled in the art will appreciate that as long as the seals 74 do not straddle the top end of the low pressure transfer tube 16, the pressure P, at the lower end 56 communicates through low pressure transfer tube 16 through cavity 88 and into cavity 90 so that the pressure Pi acts on the area of the compensating piston 76 exposed to cavity 90. A seal 92 retains the pressure P, in cavity 90 white, at the same time, allowing the compensating piston 76 to move with respect to the low pressure transfer tube 16. The low pressure transfer tube 16 is secured to the needle 27 and is placed in alignment with a longitudinal passage 94 in the needle 27. A seal 96 separates the pressure Pi, which exists in passage 94 and in low pressure transfer tube 16, from pressure P3, which exists in cavity 82.

Seal 78 serves a similar purpose around the periphery of the needle 27.

The significant components of the apparatus now having been described, its operation will be reviewed in more detail. Figures 2A-B reflect the apparatus A in the condition with the surface pumps turned off. In that condition, the spring 22 pushes the compensation piston 76 against delay valve tube 8 and, at the same time, pushes the needle 27 against the ledge formed by opening 84. At the same time the delay valve spring 10 pushes the delay valve piston 9 against hydrostatic pressures applied through the upper end 58 through the porous metal filter 7 and mud flow port 6. At this point with no flow, Pi=P2 and the delay valve piston 9 is in fluid pressure balance.

When the surface pumps are turned on, the first objective of the apparatus A of the present invention is to obtain a preload force on the needle 27 which actually compensates for the mechanical condition of the motor 50 and any other variables downhote which have affected the pressure drop experienced in the region of the drilling motor 50 and the bottom-hole assembly since the last time the pumps were operated from the surface. The desired preload acts to put a force on the needle 27 which will prevent it from rising on increasing pressure Ps until a predetermined level is exceeded. Stated in general terms, the pressure P2 is maintained at a desirably a steady level as possible by modulation of the position of needle 27 responsive to fluctuations in pressure Pi. Variations in pressure Pi will occur as a result of the drilling activity being conducted with bit 40. Accordingly, with the surface pumps turned on and the bit 40 off of bottom, meaning that there is no drifting going on, the pressure P2 increases with respect to pressure P3 as circulation is established.

When this occurs, the pressure P, also increases with respect to pressure P3. As previously stated, cavity 82 communicates with pressure P3 through the porous metal filter 26. By proper configuration of the compensating piston 76, the pressure Pi, which exceeds the pressure P3, communicates through the low pressure transfer tube 16 into cavity 88 through ports 17 and into cavity 90, and onto the top of compensating piston 76. Ultimately, an imbalance of forces occurs on compensating piston 76 due to pressure P, in cavity 90 and P3 in cavity 82 which causes piston 76 to compress the compensation spring 22. The compensating piston 76 is designed to complete its movement and reach an equilibrium position before the piston valve 15 moves downward sufficiently to bring the seal 74 over the upper end of the low pressure transfer tube 16. Figures 3A and B show the conclusion of ail the movements when the pumps on the surface are turned on and the bit 40 is off of bottom. However, the movement occurs sequentially so that the piston 76 finds its preload position, shown in Figure 3B, before movement of piston valve 15 occurs. Movement of piston valve 15 occurs as the pressure P2 ultimately communicates with cavity 62, as described previously. The fluids in the well, which have been passed through the porous metal filter 7 push on the delay valve piston 9 and ultimately the delay valve spring 10 is compressed. As previously stated, the cavity 66 is filled with a clean oil which is ultimately forced through the orifice assembly 12 into cavity 68 by movement of delay valve piston 9. The orifice assembly 12 is designed to provide a sufficient time delay, generally 1-2 minutes, so that the compensating piston 76 can find its steady state position. Those skilled in the art will appreciate that when the surface pumps are turned on and flow is initiated, it takes a little time for the circulating system to stabilize. Thus, one of the desirable functions of the apparatus A is that the low pressure transfer tube 16 is not capped by the piston valve 15 by virtue of seal 74 until the compensating piston 76 has found its desirable position shown in Figure 3B. In the position shown in Figure 3B, the forces on the compensating piston 76 have reached equilibrium.

Thus, the pressure Ps acting on the bottom of compensating piston 76 in conjunction with the force of compensation spring 22 becomes balance with the pressure Pi that is acting in the now enlarged cavity 90. Ultimately, enough clean fluid passes through the delay valve orifice assembly 12 to urge the piston valve 15 downwardly to the position shown in Figure 3A such that the seal 74 straddles the low pressure transfer tube 16. As soon as this occurs, the compensation piston 76 is in effect isolated from further fluctuations of the pressure Pi. In effect, the pressure at the lower end 56 can no longer communicate with the top end of the compensating piston 76 because the piston valve 15 has cutoff the access to cavity 90 by capping off the low pressure transfer tube 16.

After having attained the position shown in Figures 3A and B, the drilling with bit 40 begins. This puts an additional load on the motor 50 which in tum raises the pressure Pi. As the pressure P, rises, the needle 27 has a profile, which in turn decreases the pressure drop across the restrictor orifice 31 as the needle 27 moves upwardly. Due to the profiles of needle 27 as the needle moves up the pressure drop change per unit of linear movement is increased. The spring 22 resists upward movement of the modulation ram needle 27. At this point in time when the bit 40 contacts the bottom of the hole, the compensating piston 76 is immobilized against upward movement because the piston valve 15 has capped off the pressure P, from communicating with cavity 90. Since P2 is always greater than Pi due to frictional losses and the pressure drop across the orifice 31, the pressure in cavity 68, which is P2, keeps the piston valve 15 firmly bottomed in the delay valve tube 8. As previously stated, the seal 70 prevents the pressure Pz, which is in cavity 68 in Figure 4A from getting into cavity 90. Accordingly, the compensating piston 76 now is in a position where it supports the spring 22 with a given preload force on the needle 27. As the motor 50 takes a greater pressure drop, which tends to increase Pi, the upward forces on needle 27 eventually exceed the downward forces on needle 27. The downward forces on needle 27 comprise the pressure P3 acting on top of the needle 27 in cavity 82 in combination with the preload force from spring 22. Thus, an increase in the pressure Pi which exceeds Ps backs the needle 27 out of the orifice 31 removing some of the pressure losses that had been previously taken across the orifice 31. Thus, the increase in pressure drop at the motor 50 is compensated for by a decrease in pressure drop at the orifice 31 with the net result being that very little, if any, pressure change occurs as P2 remains nearly steady. In other words, the system pressure drops upstream of the upper end 58 remains steady and all that desirably occurs is an increase in pressure drop through the motor 50 compensated for by a corresponding decrease in pressure drop across the restrictor orifice 31 with the net result that the thruster 34 sees little, if any, pressure change as indicated by the symbol P2.

When the pumps are again turned off at the surface, the apparatus A quickly resets itself. As the pumps are tumed off at the surface P2 decreases, thus reducing the pressure in cavity 62. A check valve 13 allows flow into cavity 66 from cavity 68.

Accordingly, when the spring 10 pushes the piston 9 upwardly, it draws fluid through the check valve 13, which in turn draws fluid out of cavity 68. The drawing of fluid out of cavity 68 brings up the piston valve 15 and ultimately takes the seal 74 off of the top of the low pressure transfer tube 16. When this occurs, P1 can then communicate through the low pressure transfer tube 16 and into cavity 90 as previously described. Ultimately, with no fluid circulating, P3 will be equal to P, and the spring 22 will bias the compensating piston 76 back to its original position shown in Figure 2B. Therefore, the next time the surface pumps are started, the process will repeat itself as the compensating piston 76 seeks a new equilibrium position fully compensating for any changes in condition in the circulating system from the drilling motor 50 down to the bit 40.

Those skilled in the art will appreciate that the configuration of the compensating piston 76 is selected in combination with a particular spring rate for the compensating spring 22 to deliver a preload force on the needle 27 within a limited range. Too little preload is undesirable in the sense that minor pressure fluctuations in P, during drilling will cause undue oscillation of the needle 27. On the other hand, if the preload force is too great, the system becomes too insensitive to changes in Pi, thus adversely affecting the operation of the thruster 34 and if extreme enough causing the thruster 34 to load the b'rt 40 to the extent that the motor 50 will bog down and stall. Thus, depending on the parameters of the drilling motor 50 and the bit 40, the configurations of the compensating piston 76 and spring 22, as well as the profile of the needle 27 can be varied to obtain the desired performance characteristics. Similarly, the orifice assembly 12 can be designed to provide the necessary delay in the capping of the low pressure transfer tube 16 to allow the system to stabilize before the low pressure transfer tube 16 is capped.

This, in turn, allows the compensating piston 76 to seek its neutral or steady state position before its position is immobilized as the piston valve 15 caps off the low pressure transfer tube 16. In essence, what is created is a combination spring and damper acting on the needle 27. The spring is the compensation spring 22, while the damper is the cavity 82 which varies in volume as fluid is either pushed out or is sucked in through port 24 or the porous metal filter 26 which can act as an orifice in the damper system.

Those skilled in the art will now appreciate that the apparatus A provides several important benefits. It is seff-contained and it is a portion of the bottom-hole assembly. Each time the surface pumps are turned on the compensating feature adjusts the preload on the needle 27 to account for variations within the circulating system. Once in operation during drilling, the system acts to smooth out pressure fluctuations caused by changes in the drilling activity so that the pressure fluctuations are isolated as much as possible from the thruster 34. With these features in place, drilling can occur using a downhole motor. Downhole motors are desirable when using coiled tubing or when the string, even though it is rigid tubing, is sufficiently long and flexible to the extent that a downhole motor becomes advantageous. The system using the apparatus A resets quickly using the check valve feature and stands ready for a repetition of the process the next time the surface pumps are turned on.

It shouid be noted that the normal pressure drop across the orifice 31 with the bit 40 off of bottom is approximately 400 (2760 kPa) or 500 psi (3450 kPa) or better stated should equal or slightly exceed the expected maximum drilling pressure drop expected to be generated by the drilling motor at full load conditions, in the preferred embodiment.

That pressure drop is reduced during operation as the drilling motor 50 resistance increases which causes the needle 27 to compensate by backing out of the orifice 31, thus reducing the pressure drop. It should also be noted that the amount of preload provided by the compensation spring 22 needs to be moderated so as not to be excessive. Excessive preload on the needle 27 reduces the sensitivity of the apparatus A in that it requires the pressure P, to rise to a higher level prior to the apparatus reacting by moving the needle 27 against the spring 22. Thus, a higher preload on spring 22 also reduces sensitivity. Those skilled in the art can use known techniques for adjusting the variables of preload and needle profile within an orifice 31 to obtain not only the desired pressure compensation result but the appropriate first, second, and higher order responses of the control system so that a stable operation of the modulation ram needle 27 in orifice 31 is achieved, The foregoing disciosure and description of the invention are illustrative and explanatory thereof, and various changes in the size, shape and materials, as well as in the details of the illustrated construction, may be made.

Claims (16)

1. Claims 1. A bottomhole drilling assembly comprising: a fluid-operated motor for driving a bit; an extendable thruster for controlling weight on the bit during drilling; and a compensator adjacent said thruster for compensating for pressure changes created by operation of said motor and said bit, said compensator comprising a movable member which is movable to create a variable orifice; wherein said movable member has a profile arranged so that the pressure drop change per unit of linear movement increases when said movable member moves in a first direction.
2. 2. A bottomhole drilling assembly as claimed in claim 1, wherein said movable member comprises a needle.
3. 3. A bottomhole drilling assembly as claimed in claim 1 or 2, wherein said movable member has a preload bias which is automatically adjustable.
4. 4. A bottomhole drilling assembly as claimed in claim 3, wherein said preload bias is set by sensing the pressure difference between the pressure adjacent said variable orifice (P1) and the annulus pressure (P3) outside said compensator.
5. 5. A bottomhole drilling assembly as claimed in claim 4, wherein said preload bias is set by a first piston movable responsive to the pressure difference P,-P ;.
6. 6. A bottomhole drilling assembly as claimed in claim 5, wherein a first side of said first piston and said movable member define a cavity exposed to the annulus pressure P-..
7. 7. A bottomhole drilling assembly as claimed in claim 5, wherein a second side of said first piston is exposed to pressure P,.
8. 8. A bottomhole drilling assembly as claimed in claim 5 or 7, further comprising a spring disposed between said first piston and said movable member for biasing said movable member.
9. 9. A bottomhole drilling assembly as claimed in claim 6,7 or 8, wherein said cavity has a restriction in its communication with said annulus pressure P ; so as to allow fluid therein to dampen movement of said movable member.
10. 10. A bottomhole drilling assembly as claimed in any of claims 5-9, further comprising a locking device for preventing further movement of said first piston after said first piston reaches equilibrium under a pressure difference of P-P, with said bit off the hole bottom, thereby locking in a predetermined preload force on said movable member.
11. 11. A bottomhole drilling assembly as claimed in claim 10, wherein said movable member has a passage which communicates the pressure P through a tube to a second side of said first piston, said locking device selectively covering an end of said tube to isolate said second side of said first piston from the pressure P.
12. 12. A bottomhole drilling assembly as claimed in claim 11, wherein said locking device comprises a second piston which moves in sealing contact with said end of said tube after a delay long enough to allow said first piston to reach equilibrium when exposed to a pressure differential of P1-P when said bit is off the well bottom.
13. 13. A bottomhole drilling assembly as claimed in claim 12, wherein said delay is accomplished by a third piston with one side responsive to pressure adjacent said thruster (P2), said third piston displacing fluid through an orifice to said second piston at a controlled rate such that movement of said second piston and closing off said tube is delayed until said first piston is in said equilibrium position.
14. 14. A bottomhole drilling assembly as claimed in claim 13, wherein the spring with said preload from movement of said first piston allows movement of said movable member in response to fluctuation of Pi to change the orifice size so as to keep the pressure at an inlet to said compensation device P nearly steady.
15. 15. A bottomhole drilling assembly as claimed in any of claims 1-14, further comprising a MWD package.
16. 16. A bottomhole drilling assembly as claimed in claim 15, wherein said MWD package can contain both directional and a full complement of formation and seismic logging sensors.