JPS61225489A - Apparatus for remote operation of equipment combined with duct through which non-compressible fluid is recirculated, especially, apparatus for operating stabilizer of one set ofdrilling bits - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to an actuating device for remote actuation of equipment associated with a duct, and in particular to a device for actuating stabilizing devices of a set of drilling rods.

Tools used for the exploration and extraction of hydrocarbons must generate high power to carry out the drilling operation, and there must be a means to generate and control the energy required for tool operation. Must be placed at the bottom of the hole at a point very far from the top location, with one end placed on the surface;
Bottom-of-hole tools are typically supplied with an incompressible fluid, such as drilling mud, by a very large length of duct whose other end is placed at the bottom of the hole and can supply the drilling mud to the drilling tool. The end of the duct placed on the 0 surface is connected to a pumping device that makes it possible to introduce pressurized drilling mud into the duct at a certain approximately constant rate during tool operation.

Some equipment mounted at great distances from the surface and combined with ducts or drilling rods must be remotely controlled and monitored by telemetry equipment, this may be the case, for example, when inclined wells are involved. , applies to devices that allow the orientation of a drilling tool and the monitoring of its path.

It would also be desirable to provide a reliable and accurate remote actuation means for stabilization devices used in controlled passage excavation equipment.

The use of a set of rods, usually with a stabilizing device or stabilizer connected to the portion of the rod near the drilling tool, to correct the path and fully control its direction during the extension of the well path. It is known to do. These stabilizers have a body connected to a set of rods and one or more blades movable radially relative to the axes of the set of rods. The control means also allows the blade to be withdrawn towards the exterior of the stabilizer to vary the bearing distance between the axes of the set of rods and the edge of the wellbore.

The above-mentioned blades (hereinafter referred to as "support-to-fulcrum blades") reduce the radial forces exerted on the set of rods and therefore on the tool during excavation, depending on the situation (vertical excavation, inclined excavation in a given direction or direction change). It can be varied in any desired respect.

However, currently known control means capable of actuating the stabilizer have a complex structure, are difficult to use, and do not allow accurate movement and complete movement control of the inter-fulcrum blades.

Generally speaking, it is simple and completely reliable in operation, allows for remote activation of equipment associated with ducts in which pressurized fluid circulates, and allows the operation of this equipment to be controlled while at the same time being arranged close to it. No device is yet known that is compatible with a combined telemetry device.

It is an object of the present invention to provide a first end through which an incompressible fluid is conveyed by pump means at a particular operating speed, and a second end remote from said first end which uses said incompressible fluid as a working fluid, for example. an actuating device for remote actuation of equipment combined with a duct in which said incompressible fluid circulates, having a simple structure, reliable operation, It is an object of the present invention to provide an actuating device which can be used and whose actuation can be controlled without using energy other than the energy source supplied by the incompressible fluid and without actuating elements outside the duct.

To this end, the actuating device according to the invention provides for restricting the passage cross-section of the incompressible fluid in the duct in an area remote from the first end and as a function of the flow rate of the incompressible fluid. a first contoured throttle element for generating a variable head loss as, on one side receiving the pressure of said incompressible fluid upstream of said first contoured throttle element and on the other side; a differential piston mounted for axial movement within the duct in response to fluid pressure reduced by the first contoured restriction element; , contoured surfaces on the differential piston adapted to interact to increase head losses on opposite sides of the differential piston during movement of the differential piston in a first direction of movement; and a second contoured element integral with said duct, said first
means for returning the differential piston in a second direction of movement opposite to the direction of movement of the differential piston, means for determining the operating state by pressure measurement at the first end of the duct; having receiving means on said installation actuated as a result of a pressure difference between opposite sides of said differential piston, said returning means and said first contoured restricting means having a force acting on said first contoured restricting means in said duct; such as to initiate movement of the differential piston in the first direction of movement at a drive speed greater than the actuation speed of the incompressible fluid.

said duct being a set of hollow rods of a controlled passage drilling rig, said controlled passage drilling rig carrying a drilling tool fixedly attached to one of the ends of said set of hollow rods; the stabilizing device having a body connected to said set of hollow rods and at least one fulcrum-to-fulcrum blade mounted for radial movement within said body, said actuating device The differential piston of
The set of hollow rods is mounted in such a manner that not only parallel movement but also rotational movement about the axis of the set of hollow rods is possible, and for the step-by-step rotational movement of the differential piston and to its initial position. longitudinal inclines arranged in sequence around the circumference of the differential piston and radially inclined with respect to the axes of the set of hollow rods connected to each other to form a continuous working surface for the return of the differential piston; and at the end of the operation of the differential piston, for radially withdrawing the inter-fulcrum blade during the movement of the differential piston in the first direction of movement, which greatly increases the head loss of the circulating drilling fluid; The differential piston has on its outer surface at least one actuating finger which is radially movable and is mounted to interact with the continuous actuating surface on the one hand and the relative blade on the other hand.

In order to make the invention easier to understand, some embodiments of the actuating device according to the invention used for drilling oil wells and extracting oil will now be described by way of non-limiting example with reference to the drawings.

The ta is a set of rods l carrying a drilling tool 2 at the lower end
The drilling tool 2 is shown in its working position at the bottom of the hole 3. A set of hollow rods 1 form a large length duct, one end of which is connected to a drilling tool 2 at the bottom of the hole, and the other end placed on the surface and connected to a duct 4. The duct 4 can inject drilling mud into the internal space of the hollow rod 1 at high pressure and at a constant speed.

For this purpose, the duct 4 is connected to a pump device 5, on which a measuring device 6 can accurately measure the pump pressure. Drilling mud descends a set of hollow rods l to be supplied to the drilling tool 2 at the bottom of the hole 3, and then rises again to the surface through the hole 3 outside the set of hollow rods l.

The equipment 7 for directing the drilling tool 2 and the telemetry unit 8 are combined with the set of hollow rods l above the part where the drilling tool 2 is connected to the set of hollow rods l.

Pressurized drilling mud is used as a working fluid for the drilling tool 2.

FIG. 1a shows an embodiment of an actuating device according to the invention, which makes it possible to remotely control an installation (117) for orienting a drilling tool by supplying the necessary driving force to the tool. This actuating device is shown in a section 11 of a long duct formed by a set of hollow rods 1.
arranged within. This part 11 can itself consist of a connecting piece between hollow rods 1 , an end of one hollow rod or a part of equipment 7 that can be connected to a set of hollow rods 1 . This hollow part 11 has a central hole, indicated by the arrow 1.
3 receives the flow of drilling mud that circulates in the direction of 3 and reaches the drilling tool 2 at the bottom of the hole 3. 1 set of hollow rod 2 parts 1
The central hole 12 of 1 has an enlarged portion 12a in which the actuating device is mounted. This actuating device comprises a differential piston 10 of tubular profile, a return spring 15 and a profile element 16.
are arranged axially within the portion 11.

The inner bore of the differential piston IO is arranged in the direction 13 of the circulation of drilling mud.
into two successive parts, namely a first contoured part 17 forming a diaphragm introducing head losses into the duct and a truncated cone having a constricted part 18a at the end and connected to the diaphragm 17 by an annular surface. Second contour part 1 of the shape
Have a day. This contoured portion 18 may be cylindrical.

The contour element IB or needle has a conical front part 18a and a rear part 18b which makes it possible to fix the contour element 16 in the duct 11 by means of a spacer 20. In other alternative embodiments of the device in which the needle 18 is drilled with a central hole 13, the needle 16 can also be made without a central hole.

The differential piston 10 is sealingly mounted by a set of O-ring gaskets 22 in the bore portion 12a of the duct defining its chamber. The differential piston 10 has a guide installed so that it slides and is completely guided in an orifice machined in the duct 11 at its front part: ts23
It is expanding in the form of Other mechanical connections may also be made between the section 11 of the duct and the differential piston 10. Differential piston 10 is returned by spring 15 to its forward position as shown in FIG. 1a.

The force of the spring 15 causes the differential piston to be held in its forward position when the drilling mud circulates in the duct at an operating speed lower than its normal speed or the actuator's controlled speed.

The shape of the contoured front part lea of the contour element 16 is such that when the differential piston 10 moves rearwardly, i.e. from left to right in FIG. La, significant head losses occur during the circulation of the drilling mud. Due to its head loss attributable to the interaction of the contour element 16 and the contour section 18, which are designed to interact with the contour section 18 of the differential piston 10,
The total head loss of the actuator is increased considerably and very quickly.

FIG. 2 shows an operation graph of the actuating device shown in FIG. 1,
The time is plotted on the abscissa and the flow rate of drilling mud Q1, the head loss ΔP across the actuator and the differential piston 1
The zero stroke is plotted on the ordinate. The time variation of the flow rate Q during the operating cycle of the zero actuator is represented by the dashed curve 25, and the variation of the head loss ΔP is represented by the solid curve 26. , and the change in the stroke C of the differential piston 10 is represented by a curve 27 indicated by a dash-dotted line.

The origin of the graph represents the operating point when the movement of the differential piston 10 is zero at the operating speed Qs of the drilling mud.

For use of the actuator, the flow rate of drilling mud is gradually increased during the first period TA of the actuation cycle. That is, at the end of this part of the 6 working cycles, in which this flow rate is increased from 0 or Qs to the value QACT, i.e. the driving flow rate, the head loss in the first contour section, i.e. the front contour section 17, of the differential piston 10 is The value ΔPa is reached. This value corresponds to an overpressure on the front side of the differential piston IO, which generates a force that begins to exceed the restoring force of the return spring 15.

Next, the differential piston 10 moves rearward and strokes C.
+, but the flow rate is maintained at the value QACT. The head loss gradually increases from the value ΔP to the value Pb as a result of the gradual decrease in the outlet cross-section of the differential piston 10 in the second stage B of the working cycle, and then in the stroke c1 of the differential piston 10 the head loss increases gradually from the value ΔP to the value Pb. The contour section 18 is moved opposite the contour section 18a of the needle 16. Head loss ΔP
increases very quickly and the differential piston 10 moves rearward with increased speed in phase C of the working cycle. The flow rate is maintained at the value QACT by the pumping device 5, the movement of the differential piston IG is self-maintained as a result of the increased head loss, and the differential piston IO is maintained until it hits the rear of its chamber 12a by performing a stroke C2. Moving. The head loss then changes from the value ΔPh to its maximum value ΔP1. This increase in head loss is significantly greater than that which can be obtained by increasing the flow rate in a diaphragm with constant pores.

The guide 23 of the differential piston 10 is connected to a movable member of the installation 7 in order to provide an orientation angle to the excavation tool 2 .

At the same time or independently, the duct 2 in front of the differential piston 10
The overpressure ΔP of the drilling mud sampled by 4 can also be used to actuate the hydraulically actuated receiving means of installation @7.

During operation of configuration g47 with constant flow QACT, the head losses no longer increase as the force exerted by the differential piston 10 becomes insufficient to continue performing the operation.

Then, in order to finish the operation of the 0th order setting @7 in which a plateau at the value ΔPiΔP is recorded, a value Q higher than the value QAcr is required.
Just bring the flow rate to '8CT.

The maximum head loss occurs at the value Δ/p1ΔP. Thereafter, the flow can be restored and maintained at a value QACT sufficient to hold the differential piston 10 in the aft position.

As long as the flow rate is maintained at the value QACT, the differential piston 10
remains in its aft position and the head loss ΔP remains at its maximum value.

The differential piston 10 is returned to its forward position shown in FIG. 1a by gradually reducing the flow rate to a value of 0 (stage E). The drilling tool 2 can then be operated by increasing the flow rate to the value of the operating flow rate Qs, and the equipment 7 associated with the operating state is in the new state.

During the entire working cycle, the pump device 5 provides a flow rate of QA
cr and maintained at this value, and changes in the pump pressure ΔP are detected and recorded by the measuring device 6. Thus, both control and monitoring of the operating cycle is carried out from the surface without difficulty and without the use of a remote control device.

In particular, it becomes easier to detect and record the stoppage of the differential piston (which results in a pressure plateau) before the end of the operation. In this case, operation continues by increasing the flow rate to a value sufficient to release the equipment 7. The pumping means 5 must therefore be able to increase the flow rate, if necessary, to a value greater than QACT, which generally corresponds to a head loss ΔP as a function of 1 hour during the entire operating cycle of the actuating device. Differential piston 10 by recording overpressure
The position of the actuator can be ascertained and therefore the operation of the actuating device can be monitored. A recorder that records the pressure as a function of time is therefore combined with the measuring device 6.

In order to return the differential piston 10 to its initial position after the installation 7 has been activated, the flow rate due to the pumping action must be Qs
It only needs to be reduced to a smaller non-zero value, and the drilling tool 2 can then be operated by increasing this flow rate again to the value Qs.

Figures 1b, 1c and 1d show other embodiments of the actuating device, corresponding elements in Figures 1a to 1d are given the same reference numerals.

In FIG. 1b it can be seen that the differential piston 10 consists of a non-hollow member with a contoured part 31 adapted to interact with a contoured element 30 machined into the inner surface of the duct 11.
The contour element 30 performs the functions of both the diaphragm 17 and the needle 16 of the embodiment shown in FIG. 1a. The differential piston 10 has a cylindrical portion 10a with an O-ring gasket mounted so as to be movable within a chamber provided in a cylinder 35 mounted on the axis of the duct 11.

The chamber of the differential piston 10 is an annular chamber 33 coaxial with the duct 11 and closed by a flexible cylindrical diaphragm 32.
It receives pressurized working fluid at one of its ends via a conduit 34 which communicates at one end with. The pressurized working fluid acting in contact with the front face of the piston in the piston chamber is in pressure equilibrium with the drilling mud upstream of the actuator. In contrast, differential piston 1
The rear face of 0 is in contact with drilling mud at a pressure reduced by the amount of head loss introduced through 1 profile element 30.

The differential piston 10 and return spring 15 assembly is hermetically mounted within a chamber of a cylinder 35 which receives pressurized working fluid uncontaminated by drilling mud.

The actuating device operates in substantially the same way as the actuating device shown in FIG.
P is sufficient to move the differential piston 10 in the flow direction (arrow 13) as soon as the flow rate reaches the value QACT.
The head loss is increased due to the interaction with the differential piston 10, so that the differential piston 10 moves to its end position.

As previously mentioned, drilling mud under overpressure is withdrawn via the duct 24 to operate the equipment 7 associated with the duct 11.

FIG. 1c shows an embodiment of an actuating device combining the same elements of the actuating device of FIG. 1b in a different arrangement;
The chambers of the cylinder 35 and the differential piston 10 are oriented in opposite directions relative to the drilling mud circulation (arrow 13). Annular chamber 33
, the closed circuit comprising the duct 34 and the chamber of the differential piston 10 contains a pressurized working fluid completely insulated from the drilling mud, and the contour element 30 of the duct 11 causes the differential piston to move when the flow rate reaches the value QACT. Introducing a head loss that can initiate the movement of water. The contour 31 of the differential piston 10 then interacts with a contour element 30 which performs the functions of both the diaphragm 17 and the needle 16 of the embodiment of FIG. 1a.

As previously mentioned, the overpressure ΔP is recovered via the duct 24 in order to operate the installation @7.

In the embodiment shown in FIG. 1d, the differential piston 10 has a tubular shape similar to the differential piston shown in FIG.
It has a pair of contour sections 17,18.

The frustoconical contour section 18 connects the duct 37 and the blocking element 3
Reduct 1 by spacer 38 that can fix 6
1 interacts with a blocking member 36 in order to gradually close a duct 37 coaxially fixed within 1.

As soon as the flow rate reaches the value QACT, the differential piston 10 moves backwards, the contour section 18 closes the deformable member 36 and at the same time increases the head loss, so that the differential piston 10 moves to its end position. It moves and hits the rear stop.

In the apparatus shown in FIGS. 1b, 1c and 1d, the differential piston 10 can be returned to its initial position by reducing the flow rate to a low value that can be reduced to zero.

FIG. 3 shows a drilling rig comprising a set of drilling rods 51 carrying a drilling tool 52 at the lower end and connected at the other end by a duct 54 to a pumping device 55, the pumping device 55
Drilling mud can be injected into the tool in the bottom working position of 3 through the inside of a set of drilling rods 51.

As seen in FIG. 1, the pair of rods 51 are connected to each other, and the stabilizer 57 and the connecting member 58
51 connected to the drilling tool 52 by an intermediate element including
Contains continuous rods such as a, 51b.

Above the pump device 55, a means for measuring the pump pressure of drilling mud, that is, a pressure measuring device 5B is arranged.

In particular, a measuring unit 58 is associated with the drilling tool 52, which is capable of measuring the orientation of a set of rods 51.

Figure 4 shows a stabilizer, generally designated by the reference numeral 57, which connects itself to a set of rods 51 or drilling tools by a threaded connection such as 59. A tap end 81a that can be
It includes a generally tubular body portion 60 having an Eflb. When the stabilizer 57 is connected to one set of rods 51, the axis B2 of the hole 63 in the main body BO is aligned with the one set of rods 5.
It is the same as the axis of 1. Drilling mud circulates axially through the set of rods 51 and stabilizers 57 in the direction of arrow 84.

As seen in FIGS. 4 and 5, the body portion 60 has a recess 6 that allows the drilling mud to pass outside the stabilizer 57 as it returns to the surface within the hole 53.
5 on its outer surface also has a hole 66 that serves to accommodate an inter-fulcrum blade 68.

The stabilizer shown in FIGS. 4 and 5 has three inter-fulcrum blades 68 arranged at 120 DEG around its body. As shown in FIGS. 4 and 5, the leaf spring 71 whose one end is fixed to the main body 70 with a screw is
The other end of leaf spring 71 abuts the end of inter-fulcrum blade 68 to hold inter-fulcrum blade 68 in a radially retracted position.

A closing member 72 mounted at the end of the hole 66 outside the leaf spring 71 can guide the inter-fulcrum blade G8 in its radial movement direction. The fully retracted position of the blade between the fulcrums shown in FIGS. An assembly play is provided between the leaf spring 71 and the closure member 72 to allow a specific movement of the inter-fulcrum blade 68 in the radial direction between the extended or extended position of the inter-fulcrum blade 68. There is. Each actuation finger 69 is connected to the body 6 by an O-ring gasket 70.
It is movably attached in a sealed state within 0.

A tubular piston 75 is installed within the hole 63 of the main body portion 60 . This piston 75 has two parts 75a and 75b which are hermetically joined to each other by screws 7B and gaskets 77 to enable mounting. Piston 75 is slidably mounted within bore 63 by two O-ring gaskets 78 arranged on a portion of its circumference and at its ends.

Portion 75 of piston 75 within portion 75a of piston 75
A pole-thrust bearing 60 is placed at the end of b, against which one end of a helical spring 81 rests, and the other end of this helical spring 81 rests in a stop fixed to the body 60 in the hole 63. I hit 62 and did X.

An annular profile member 84 is also mounted within the end of the portion 75b of the piston 75 corresponding to the inlet of circulating drilling fluid in the direction of arrow 64.

A second contour member or needle 85 is located at the hole 63 in the body portion 60.
are arranged within the main body part 60 at the axes of l and n. The needle 85 is secured within the body portion 60 by an annular support member 86 having a radial spacer 87 for securing it.

Drilling fluid circulating in the direction of arrow 64 produces a head loss as a function of its flow rate as it enters piston 75 via the inlet of profile member 84. At a particular flow rate, called the driving flow rate, the pressure difference on either side of the piston 75 is sufficient to exert a force on this piston 75 that is greater than the force of the helical spring 81, so that the piston 75 moves axially in the direction of arrow B4. The inner contour of the zero profile member 84 that begins to move in the direction interacts with the outer contour of the needle 85 to gradually reduce the passage cross-section of the drilling fluid and increase the head loss proportionately. At the end of the movement of the piston 75, the head loss becomes so large that it reaches a value that can be easily detected in the pumping device 55 by means of the pressure measuring device 5B associated with the pumping device 55.

The movement of the piston 75 is therefore controlled by the flow rate of fluid forced by the pump and is completely monitored from the surface by pressure measurements.

Such a remote actuation device has a high stability, since the head loss generating the force for moving the piston 75 increases continuously during the movement of this piston.

The outer surface of the piston 75 is machined with two sets of actuation ramps 90 and 91 spaced longitudinally from each other on the piston 75, each of which is placed on one of the ends of the interfulcrum blade 68. Interacts with an assembly of three actuation fingers 68.

The actuation ramps 90 and 81 are radially inclined in the same direction relative to the axis 62 common to the piston 75 and the bore 63.

This inclination causes the piston 75 to move in the direction of arrow 64.
The inter-fulcrum blades 68 can move radially while the fulcrum blades 68 move axially.

Looking at FIG. 5 and FIG. 6, the continuous inclined surface 90a,
It can be seen that 90b and 9Qc are arranged one after another over the circumference of the piston 75.

A complete cycle of movement of the inter-fulcrum blade 68 is obtained by three successive ramps 90a, 90b and 90c;
The machining depth at their ends from the outside diameter of the piston 75 is zero actuation fingers 69, shown at 10-3 cm in FIG.
are each maintained in contact with the bottom of the ramp assembly 60 by means of an end machined in the form of a spherical bearing surface, via a leaf spring 71 of the corresponding inter-fulcrum blade 68.

As seen in FIG. 6, the actuating finger 69 and ramp 9
As a result of the interaction 0a, the piston 7 in the direction of arrow 83
5 allows the end of the actuating finger 69 to move from level -11 to level -8. Similarly, the inclined portion 90b
Accordingly, the actuating finger 68 moves from level-6 to level-4,
You can move to 5.

These two movements on the ramps 90a and 90b are therefore achieved by a radial movement of the actuating finger 69 towards the outside of the body portion 70 and thus by an outward movement of the inter-fulcrum blade 68.

In fact, as can be seen in FIG. 5, the distribution of the ramps over the circumference of the piston 75 is such that at each moment all actuating fingers 69 are in contact with a set of identical ramps, and the distribution of these actuating fingers 69 in the radial direction The movement of is therefore such that it is the same at each instant. The ramp 90c corresponds to the movement of the actuation finger 69 from levels -4, 5 to level -11;
corresponds to the return of the blade 68 to its initial position and the return of the interfulcrum blade 68 to its retracted position.

Thus, each of the three actuating fingers 68 of assembly θ0 shown in FIG.
The total number of ramps making up the zero assembly 60 that performs a complete travel cycle for c is therefore 3X3=9.

From FIG. 5 and FIG. 6, the inclined parts 90a, 90b, 90
It can be seen that c are connected to each other by a curved member 94 and by a level straight member 95 to form a continuous working surface 96 arranged around the circumference of the piston ψ5. A curved member S that joins the end of the inclined portion 30 to the end of the straight member 95
4 can rotate the piston 75 step by step in the direction of the arrow 98 as a result of the interaction of the actuating finger 69 and the bending member 94 at the end of the movement of the piston 75 in one direction or the opposite direction. Each rotation step thereof is equal to the angular distance between the inclined part 60 and the adjacent planar straight member S5, ie: 31110'/18=20°.

In one direction, the driving force is generated as a result of the head loss of the drilling fluid, and in the opposite direction, the driving force is generated by the energy stored in the spring 81.

Step-by-step rotation of the piston 75 can occur only in the direction of arrow θ8. This is because the free φ wheel 100 (FIG. 4) is installed in the hole 63 of the main body BO around the portion 75b of the piston 75.

The piston 75 is integrated in rotation with the freewheel 10G by means of a key that engages in a longitudinal keyway 101 machined into the part 75b of this piston. Therefore, the piston 75 moves longitudinally relative to the freewheel 100 under the action of the drilling fluid and the spring 81.
Execute the movement in the forward and backward direction.

Thus, as a result of the circulating drilling fluid, each longitudinal movement of the piston 75 in the direction of arrow 84 causes the bearing blade 68 to move in the extension direction (two successive steps) and in the retraction direction (one longitudinal movement step). A radial movement occurs. Since the steps of the longitudinal movement of the piston 75 are recorded on the surface, the exact position of the bearing blade 68 is ascertained and the stabilizer can be monitored very effectively. The sharp increase in pump pressure at the end of each longitudinal drive of the piston 75 makes it very easy to record the steps in the manner shown.

The operating mode of the actuator is as follows: When the inter-fulcrum blades 68 are in their respective retracted positions, as shown in FIGS. 4 and 5, a set of flows at least equal to the actuator drive flow rate is transmitted to the rod 51 of the piston 75, thus moving the piston 75 until it reaches its end position,
Head loss increases automatically and progressively. piston 75
The end of the travel step of the piston 75 can be determined by recording the pressure from the zero surface where the head loss is at a maximum when the piston 75 reaches its end position. If the inter-fulcrum blade 68 is extended a sufficient amount, the actuator will automatically be held in place unless the drilling fluid supply flow rate is counteracted. When a further step is to be performed to extend the inter-fulcrum blade 68 by a further amount, the drilling fluid supply flow is overridden and the piston 75 returns to its initial position as a result of the action of the spring 81. Meanwhile, rotation of the piston 75 over 20' causes the actuating finger 6 to
9 could be positioned on the flat portion 25 of the operating surface 38.

At the end of the flat part 85, the piston 75 can be rotated by 20° again in the desired direction by the free wheel 100 due to the curved part θ4 of the actuating surface 138, so that the actuating finger 83 joins the next inclined part 90b. Align in a straight line. As a result of the increase in the drilling fluid flow rate up to the value of the drive flow rate, the piston 75 is moved in the direction of arrow 83 and the actuation finger 69 and inter-fulcrum blade 68 are moved outwardly and radially a further l step. Obviously, as a result of the actuation finger 68 successively passing through the flat part 95 and the inclined part 90c of levels -4, 5, the actuating device can return to its initial state.

All these movements can be fully tracked from the surface by recording the pressure.

The main advantages of the actuating device according to the invention are clear from the description just given. This means that no remote control means are necessary, since the actuating device is actuated and monitored by the use of pumping and measuring means, which are usually combined in a long duct, and the actuating device is particularly simple and reliable in operation. This actuator is operated by a very simple actuation that can be easily monitored and does not require the use of any elements other than those placed in the duct during installation of the actuator.

If the actuating device is used to control a stabilizing device,
The continuous movement of the inter-fulcrum blade 68 in one direction or the other is fully monitored and occurs under very good stability conditions.

On the other hand, a single actuator has a relatively small overall size despite its many capabilities.

The invention is not limited to the embodiments described above, but on the contrary includes all other alternative shapes.

The piston and the contour elements associated therewith can therefore have a shape different from that described above. The first profile element can be combined with the piston or, conversely, independent of this piston. This first contour element can be separated from or merged with the second contour element. The shape of these contour elements can also be different from the shape described in E.

The intention of using these shapes is to ensure that the pressure/time graph and the maximum head loss P- correspond to the operating conditions of the installation in which the actuating device is combined.

The means for returning the piston may be different from a mechanical spring.

The means for receiving the driving force or pressure difference of the piston provided in the installation 7 can have any shape that makes it possible to transmit this driving force to the active elements of the installation 7.

The operating cycle of the drilling tool can be different from that mentioned above, in particular the phase preceding the rapid movement of the piston corresponding to a sudden increase in head loss can be accompanied by a very low head loss. ,Therefore, it is possible to clearly separate the inactive stage from the active stage of the equipment.

As far as the device for actuating the stabilizer is concerned, the number of different successive ramps forming a set of ramps may be different from three if the movement is to be carried out in a series of steps less than or more than three. It can be done.

Fewer than three inter-fulcrum blades can be used and, if appropriate, the stabilizer can be provided with one inter-fulcrum blade in combination with other fixed blades or used without a combination, or vice versa. More than three blades can also be used. It is also possible to use blades aligned in the axis of a set of rods or blades inclined to this axis.

In any case, the number of ramps arranged around the circumference of the differential piston is equal to the number of blades multiplied by the number of different movement steps of the blades in the radial direction.

The inter-fulcrum blades can also be mounted differently than described above, and blades of different shapes can also be used.

Means other than free wheeling can also be combined with the differential piston to prevent it from rotating in one direction and to allow it to rotate in the opposite direction.

A drilling rig according to the invention may incorporate any number of stabilizers each comprising any number of blades, at least one of which is radially movable.

Generally speaking, the equipment to be operated includes a device for orienting a drilling tool or a device for stabilizing a set of rods, as well as a device for drilling a hole in a casing or a well or borehole using overpressure resulting from head losses. The actuating device according to the invention may consist of a device for inflating a sealing diaphragm of a The present invention can be used in other fields to distribute incompressible fluids using long ducts with limited access to water.The invention is particularly useful for water distribution or irrigation. In this case, the equipment associated with the duct is a manifold valve that makes it possible to transfer one distribution water from one duct to another.

This actuation is easily carried out by increasing the water flow rate to a level above the working flow rate, then reducing this flow rate to a very low level or zero, and increasing the flow rate again to a level corresponding to the working flow rate. can do. Of course, the reverse operation can then be performed by increasing the flow rate again above the operating flow rate to the driving value.

Very generally, the invention applies to all cases where a fluid is used as a working fluid in long ducts that are at least partially inaccessible, and also for long ducts with inaccessible parts. Used in all cases where fluid is distributed through a duct.

[Brief explanation of the drawing]

FIG. 1 is a schematic illustration of a drilling rig incorporating equipment that can be operated with a device according to the invention. Figures 1a, 1b, 1c and 1d show longitudinal sections of four different embodiments of an actuating device according to the invention. FIG. 2 is an operating graph of the actuating device shown in FIG. 1a, showing the time evolution of various characteristic parameters during the operating cycle of the actuating device. FIG. 3 is an overall schematic diagram of a controlled passage excavation rig having a stabilizer controlled by an actuation device according to the invention. 4 is a longitudinal cross-sectional view of the stabilizer of the drilling rig shown in FIG. 3 along line IV-IV in FIG. 5; FIG. FIG. 5 is a cross-sectional view of the stabilizer taken along line v--■ in FIG. 4. FIG. 6 is an exploded view of the operating surface, blade and piston of the stabilizer. [Explanation of symbols of main parts] 1 set of hollow rods・・・・・・・・・・・・・・・・・・
・・・・・・1 Excavation tool・・・・・・・・・・・・・・・・
・・・・・・・・・・・・・・・・・・2 holes・・・・・・
・・・・・・・・・・・・・・・・・・・・・・・・
・・・・・・・・・・・・3 ducts・・・・・・・・・・
・・・・・・・・・・・・・・・・・・・・・・・・
・ 4 pump device・・・・・・・・・・・・・・・・・・
・・・・・・・・・・・・・・・5 Measuring device・・・・・・・
・・・・・・・・・・・・・・・・・・・・・・・・
・8 tools with orientation are equipment...
・・・・・・7 Telemetry unit・・・・・・・・・
・・・・・・・・・・・・8 differential piston・・・・・・・
・・・・・・・・・・・・・・・・・・・・・10 ducts・・・・・・・・・・・・・・・・・・・・・・・・
・・・・・・・・・・・・11 Central hole・・・・・・・・・
・・・・・・・・・・・・・・・・・・・・・・・・
・・12 Return spring・・・・・・・・・・・・・・・・
・・・・・・・・・・・・・・・15 contour elements...
・・・・・・・・・・・・・・・・・・・・・・・・
・・・・・・16 First outline part・・・・・・・・・・・・
・・・・・・・・・・・・・・・17 Second contour part...
・・・・・・・・・・・・・・・・・・・・・18 Contour elements・・・・・・・・・・・・・・・・・・・・・・・・
・・・・・・・・・30 Contour part・・・・・・・・・
・・・・・・・・・・・・・・・・・・・・・・・・3
1 diaphragm・・・・・・・・・・・・・・・・・・
・・・・・・・・・32 Annular chamber・・・・・・・・・
・・・・・・・・・・・・・・・・・・・・・・・・33
Conduit・・・・・・・・・・・・・・・・・・・・・
・・・・・・・・・・・・・・・34 Cylindrical part・・・・・・
・・・・・・・・・・・・・・・・・・・・・・・・
...35 new elements...
・・・・・・・・・・・・・・・・・・36 ducts...
・・・・・・・・・・・・・・・・・・・・・・・・
...371 sets of drilling rods...
・・・・・・・・・・・・・・・5117 Roy Tools --
−−−・−・ −−−−−−−−−−−−−−−−−−
−−−−−−52 Pump device・・・・・・・・・・・・
・・・・・・・・・・・・・・・・・・55 Pump pressure measuring device・・・・・・・・・・・・・・・・・・5
6 Stabilizer・・・・・・・・・・・・・・・・・・
・・・・・・・・・571 sets of rod orientation measuring device・
・・・・・・58 Main body・・・・・・・・・・・・・
・・・・・・・・・・・・・・・・・・・・・60 fulcrum blades・・・・・・・・・・・・・・・・・・・・・
・・・68 actuation finger ・・・・・・・・・・・・
・・・・・・・・・・・・・・・69 Closing member・・・・・・
・・・・・・・・・・・・・・・・・・・・・・・・
・・・72 Tubular piston・・・・・・・・・・・・
・・・・・・・・・・・・75 Second contour member・・・・・・
・・・・・・・・・・・・・・・・・・85 Annular support member・・・・・・・・・・・・・・・・・・・・・
・・8G operation slope portion・・・・・・・・・・・・・・・・
...9G, 90a, 90b, 90c continuous operation surface...Pa...
・・・・・・96 Free Wheel・・・・・・・・・
・・・・・・・・・・・・100FIG, 1c Procedural amendment (formality) April 14, 1985 Director General of the Patent Office Michibe Uga 1, Indication of the case 1986 Patent Application No. 349
No. 2, Title of the invention 3, Relationship with the case of the person making the amendment Name of patent applicant NISMF International 4,
Agent March 5, 1986 (Shipping date: March 25, 1986)
(1) I would like to submit one amended application form stating the name of one representative in paragraph 3 of the application submitted on January 7, 1986. (2) As attached, power of attorney and its translation Koban 1
We will submit a notification. (3) As shown in the attached sheet, we will submit one printable copy of the full statement.

Claims (1)

Claims: 1. A first end through which an incompressible fluid is conveyed by the pump means (5) at a particular operating speed; operation for remote operation of equipment associated with a duct (1, 11) having a second end remote from the end and in which said incompressible fluid circulates; Apparatus, comprising: in the duct (1, 11) in a region remote from the first end, restricting the passage cross-section of the incompressible fluid and variable as a function of the flow rate of the incompressible fluid; First contoured throttle element (17, 30, 60
), on one side receiving the pressure of said incompressible fluid upstream of said first contoured restriction element (17, 30, 60) and on the other side said first contoured restriction element ( 1
a differential piston (10, 50) mounted so as to be axially movable within said duct in response to fluid pressure reduced by said incompressible fluid passageway (7, 30, 60); provided on said differential piston and adapted to interact to limit and increase head losses between opposite sides of said differential piston substantially during movement of said differential piston in a first direction of movement; Contoured faces (18, 26,
31, 60) and a second contoured element (16, 30, 56) integral with said duct (1, 11, 46); means (15, 55) for returning the differential piston; means (6) for determining the operating state by pressure measurement at the first end of the duct (1, 11); and , 50) or as a result of a pressure difference between the two sides of said differential piston; said returning means (15, 55); the force with said first contoured restriction (17, 30, 60) is at a driving speed Q_ greater than the actuation speed of said incompressible fluid in said duct;
Apparatus such as to initiate movement of said differential piston in said first direction of movement at A_C_T. 2. The actuating device according to claim 1, wherein the differential piston (10) has a tubular shape, the central hole of which is arranged in the direction of circulation of the incompressible fluid with the first profile. a diaphragm (17) forming an element of said duct (
11) and a surface (18) adapted to interact with said second contoured element (16) integral with said actuating device. 3. Actuating device according to claim 1, characterized in that said duct (11) has a contoured throttle element (
30), and the differential piston (10) comprises:
a contoured surface mounted in a cylinder (35) in the central part of said duct and adapted to interact with a contoured surface (30) forming both said first and second contoured elements; (31) An actuating device having: 4. An actuating device according to claim 3, which provides a space completely separated from the incompressible fluid circulating in the duct (11) and filled with pressurized working fluid. Said cylinder with a differential piston installed inside (
at least one duct (35) confining with a chamber (35);
4) and a first side of said differential piston opposite said contoured surface (31) by a diaphragm (32);
10a) to which the pressure of the incompressible fluid upstream of the differential piston is transmitted. 5. Actuating device according to claim 4, wherein the contoured surface (30) is arranged upstream of the assembly consisting of the cylinder (35) and the differential piston (10). Actuation device. 6. Actuating device according to claim 1, characterized in that the differential piston (10) has a tubular shape and that during the movement of the differential piston (10) the a first profile in which the bore of the differential piston (10) forms a diaphragm for the incompressible fluid flowing in the flow direction of the incompressible fluid, in order to change the passage cross-sectional area of the incompressible fluid; Actuating device continuously having an enlarged surface (18) interacting with a contoured element (17) and a deformable second contoured element (36). 7. An actuating device according to any one of claims 1 to 6, characterized in that the means (6) for determining the operating state by means of pressure measurements adjust the position of the differential piston at each movement. An actuating device comprising a recorder for recording the pressure of said incompressible fluid as a function of time in order to be verifiable. 8. The duct is a set of hollow rods (51) of a controlled passage drilling device, and the drilling device carries a drilling tool (52) fixedly attached to one of the ends of the hollow rod; The equipment to be operated is connected to the set of hollow rods (5
1) and a body part (60) having a central hole (63) coaxial with the holes of these hollow rods (51); An actuating device according to claim 1, characterized in that the differential piston of the actuating device (75) is a stabilizing device (57) having at least one inter-fulcrum blade (68), wherein the differential piston of the actuating device (75) is as well as the axis (62) of the set of hollow rods (51).
) is mounted in the central hole (63) of the body part (60) for gradual rotational movement of the differential piston (75) and its initial position. Continuous working surface for return to (96)
are connected to each other by alignment members (94, 95) and arranged in sequence around the differential piston (75) to form a radial direction with respect to the axis (62) of the set of hollow rods. at the end of the operation of the differential piston (75) in the first direction of movement, which significantly increases the head loss of the circulating drilling fluid. ) is radially movable within said body part (60) for radially withdrawing said inter-fulcrum blade (68), on the one hand with said continuous working surface (96) and on the other hand with said inter-fulcrum blade (68). Blade (68
), wherein said differential piston is provided on its outer side with at least one actuation finger (69) mounted for interaction with said differential piston. 8. An actuating device according to claim 8, comprising means (100) for preventing the differential piston (75) from rotating in one direction and allowing it to rotate in the opposite direction. ) is combined with said differential piston (75). 10. An actuating device according to claim 9, comprising:
Said means (100) is a free wheel mounted in said central hole (63) of said body part (60) of said stabilizer around said differential piston, said differential piston (75) An actuating device which is integral in rotation with respect to the free wheel (100) and free in translation, allowing a gradual rotational movement of said differential piston (75). 11. An actuating device according to any one of claims 8, 9 and 10, wherein the elastic means for returning the inter-fulcrum blade (68) to its retracted position ) and the blade between the fulcrums (
Actuating device consisting of a leaf spring (71) at the end of 68). 12. An actuating device according to claim 11, wherein the closing member (72) is connected to the main body (60) of the stabilizing device.
The inter-fulcrum blade (68) is guided in a hole (66) made in the body part (60) of the stabilizing device, arranged above the leaf spring (71) towards the outside of the stabilizer. actuating device that is maintained. 13. An actuating device according to claim 8, comprising:
Said stabilizing device has three successive blades (68) above the circumference of its body part (60), each of which is associated with two actuating fingers (69), said actuating fingers (69) having two arranged in pairs, the actuating fingers of which are maintained in contact with an actuating surface (66) each having a ramp (90 or 91), said two sets of actuating fingers (69) and said two actuating surfaces (96) actuating devices arranged longitudinally apart from each other with respect to said differential piston (75); 14. An actuating device according to claim 8, comprising:
The head loss generating alignment means carried by the body (60) of the stabilizing device (57) and the differential piston (75) consist of a contoured annular surface (84) and a needle (85), respectively. , the axis of rotation thereof is the axis (62) of the set of hollow rods, and the alignment means (84, 85)
) as a result of an increase in the flow rate of said drilling fluid to a threshold called actuation speed, said differential piston (75)
Drilling rig forming means for controlling the movement of. 15. An actuating device according to claim 8, comprising:
Drilling rig comprising a pumping device (55) for said drilling fluid and means (56) for measuring the pressure of said drilling fluid. 16. An actuating device according to claim 8, comprising:
Drilling rig comprising at least two stabilizing devices (57) coupled to the set of hollow rods (51) at axially spaced apart locations along the set of hollow rods. 17. Actuating device according to any one of claims 1 to 5, characterized in that the equipment (7) is a drilling tool (2) fixed to the ends of a set of rods (1) of large length. ) is an actuating device that is a device for directing