US3802515A - Device for automatically regulating the operation of a drilling turbine - Google Patents

Device for automatically regulating the operation of a drilling turbine Download PDF

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Publication number
US3802515A
US3802515A US00269733A US26973372A US3802515A US 3802515 A US3802515 A US 3802515A US 00269733 A US00269733 A US 00269733A US 26973372 A US26973372 A US 26973372A US 3802515 A US3802515 A US 3802515A
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Prior art keywords
turbine
shaft
fluid
inlet
tool
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US00269733A
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English (en)
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M Flamand
R Lazayres
P Morin
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IFP Energies Nouvelles IFPEN
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IFP Energies Nouvelles IFPEN
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    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B4/00—Drives for drilling, used in the borehole
    • E21B4/02—Fluid rotary type drives
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/20—Hydro energy
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S415/00—Rotary kinetic fluid motors or pumps
    • Y10S415/903—Well bit drive turbine

Definitions

  • the device includes a duct in the form of a bore provided in the shaft of the turbine wherein the lower part of the bore terminates in the immediate vicinity of the tool, a first communicav ing member directly connecting the source of fluid with an inlet of the turbine to provide a flow path for the hydraulic fluid therethrough and a second communicating member-for providing a flowpath for hydraulic fluid to the tool.
  • the second communicating member includes at least one orifice having a variable cross section for communicating between the inlet of the turbine and the upper end of the duct, the cross section being variable'in accordance with an operating parameter of the turbine to regulate the flow of hydraulic fluid to the inlet of the turbine and to the tool.
  • turbo-drilling requires means for regulating automatically the operating parameters of a drilling turbine.
  • One of these regulating means consists in providing the turbine with blades such that the drop of the driving pressure in the turbine decreases with the speed of rotation when the rate of flow remains constant, and in causing the flow that supplies or feeds the turbine to vary inversely with respect to the pressure for supplying the turbine a torque and power supplementwhen the speed of rotation decreases.
  • the hydraulic power lost by the turbine in the form of pressure may be compensated for by assuring the circulation of the hydraulic fluid with the aid of pumps that are capable of automatically compensating the pressure variations by means of flow variations, such as, for example, axial pumps or pumping groups driven by Diesel motors and equipped with a torque converter.
  • Another solution for regulation consists in assuring flow variations for compensation of the pressure variations of the turbine by installing in proximity to the turbine and above the latter with respect to the trepan, a reservoir at the inside of which the pressure of the drilling fluid exerts itself.
  • This reservoir whose volume is expansible in an elastic manner by virtue of deformable membranes serves as a flow-regulating fly-wheel by accumulating a certain volume of fluid under pressure which is restored at the time of a pressure drop at the inlet of the turbine, due to, or because of an'operating drop.
  • a regulating device for the automatic regulation of the operating or functioning system of a hydraulic turbine having an internal pressure drop which decreases with the rotational speed, wherein the turbine drives a tool and hydraulic fluid is delivered at an essentially constant rate of flow from a fluid source.
  • the regulating device comprises a duct formed by a bore provided in the shaft of the turbine and terminating with its lower part in the immediate vicinity of the tool, a first member directly connecting the source of fluid with the inlet of the turbine, a second member causing the inlet of the turbine and the upper end of the duct to communicate by means of at least one orifice having a regulable cross section which varies as function of the pressure of the hydraulic fluid at the inlet of the turbine in order to allow for irrigation of the tool by a portion of the flow or discharge of the hydraulic fluid.
  • the first and second members respectively include a rigid cylindrical body or element, one of they ends of which is integrally connected with the turbine and the other end of which is integrally connected with a conduit or pipe connected to the source of fluid, and of an annular reservoir concentrically positioned within the aforementioned body or element.
  • the reservoir is provided with a rigid external wall which together with the aforementioned body defines a first space through which the hydraulic fluid flows from the source of fluid toward the inlet of the turbine, and with an internal wall defining the orifice for the flow of the fluid from the first space toward the bore of the turbine shaft.
  • the internal wall of the reservoir is formed of a material which is deformable under a pressure differential applied to the internal wall, and the reservoir is filled with a gas whose pressure is equal to the pressure of the hydraulic fluid-at the inlet of the turbine corresponding to the system operation of the turbine.
  • the first member includes a rigid cylindrical body or element,one of the ends of which is integrally connected with the turbine and whose other end is integrally connected with a conduit connected with the source of fluid, and the second member includes a first cylindrical sleeve coaxially positioned with respect to this body.
  • the lower part of the first cylindrical sleeve is in communication with the bore of the shaft of the turbine and a second cylindrical sleeve closed at the upper part thereof is mounted on the first sleeve such that the sleeves nest within each other and are adapted to be displaced with respect to one another at least in the direction of their axis,
  • the cylindrical walls of these sleeves are provided with orifices which cooperate with each other so as to form an orifice having a variable cross section establishing a communication between the bore and the inlet of the turbine as function of the relative position of the two sleeves.
  • elastic means is interposed between the sleeves for controlling the displacement of one of these sleeves as function of the pressure at the inlet of the turbine.
  • a device for the automatic regulation of the operating or functioning system of a hydraulic turbine wherein the turbine drives a tool and hydraulic fluid is delivered at a constant rate of flow from a fluid source.
  • the device of this embodiment comprises a duct including a bore provided in the shaft of the turbine and terminating with its lower part in the immediate vicinity of the tool, a first member directly connecting the source of fluid with the inlet of the turbine, and a second member for communicating between the inlet of the turbine and the upper end of the duct by means of at least one orifice having a regulable cross section which varies as function of the speed of rotation of the shaft of the turbine and which permits irrigation of the tool by a portion of the flow of the hydraulic fluid.
  • the first member includes a rigid cylindrical body or element, one end of which is integrally connected with a conduit connected with the source of fluid
  • the second member includes the bored shaft of the turbine having at least one orifice provided on the lateral wall of the shaft and at the level of the aforementioned body.
  • the orifice is obstructed by a deformable resilient element having one end secured on the shaft, with the other end of the element being free such that upon rotation of the shaft, the centrifugal force exerted on the element causes the element to deform and the free end to progressively uncover or expose the orifice.
  • the regulating device comprises a first member in the form of a rigid cylindrical body, one end of which is integrally connected with the turbine and the other end of which is integrally connected with a conduit connected with the source of fluid, and a second member including a plurality of resilient elements or laminae having one end integrally connected with the shaft of the turbine and forming an essentially fluid-tight prism in the absence of rotation of the shaft.
  • the laminae are adapted to be deformed due to the action of the centrifugal force produced by the rotation of the rotor so as to become separated or spaced from each other so as to permit communication between the bore of the shaft and the inlet of the turbine.
  • the regulating device comprises a first member in the form of a rigid cylindrical body having one end integrally connected with the turbine and the other end integrally connected with a conduit connected to the source of fluid, and a second member including a first cylindrical sleeve integrally connected with the shaft of the turbine and communicating with the bore of this shaft, and a second cylindrical sleeve closed at the upper part thereof and mounted on the first sleeve such that the sleeves nest within each other and are adapted to be displaced with respect to one another at least in the direction of the axes thereof.
  • the cylindrical walls of these sleeves are provided with orifices cooperating with each other so as to form the orifice having a variable cross section for establishing communication between the bore of the shaft and the inlet of the turbine as function of the relative position of the two sleeves.
  • the second sleeve is connected with the shaft of the turbine by means of at least one elastically deformable element which deforms as a result of a centrifugal force, the deformation of this element causing a relative displacement of the two sleeves.
  • FIG. 1 schematically illustrates the device according to the present invention arranged in a slow drilling turbine wherein the internal pressure drop decreases with the speed of rotation;
  • FIG. 2 illustrates the device of FIG. 1 on an enlarged scale
  • FIG. 3 schematically illustrates a second embodiment of the device according to the present invention and arranged in a slow drilling trubine wherein the internal pressure drop decreases with the speed of rotation;
  • FIG. 4 schematically illustrates a third embodiment of the device according to the present invention which may be arranged in any type of turbine;
  • FIG. 5 schematically illustrates a fourth embodiment of the device according to the present invention which may be arranged in any type of turbine;
  • FIGS. 5A, 5B, and 5C are cross-sectional views taken along line 5- 5 in FIG. 5 showing the operating positions of the device as function of the operation of the turbine.
  • FIG. 6 schematically illustrates another embodiment of the device according to the present invention which is adaptable to any type of turbine.
  • FIG. 1 a regulating device provided in a drilling turbine whose pressure at the inlet varies with the functioning or operating system, such as, for example, turbines with special bladings (the Z type) whose internal pressure drop decreases with the speed of rotation.
  • a drilling or. boring tool 1 has been schematically shown which is driven in rotation by a turbine 2 equipped with a regulating device according to the present invention, the unit or assembly thus formed being suspended at the end of a drilling column 4.
  • the device 3 is of the by-pass type and includes a body 5 connected by any known means, for example screwed connections, with the drilling column 4 and with the turbine 2.
  • a reservoir 7 is secured at the interior of the body S-and essentially in the extension of the axis 6 of the turbine 2.
  • the reservoir has an essentially annular shape, which delimits in the body 5 two distinct concentric spaces, an essentially cylindrical space 8 in the center of the reservoir 7, and an annular space 9 arranged between the reservoir 7 and the wall of the body 5.
  • the annular space 9 serves for communicating between the drilling column 4 and the inlet of the turbine 2, whereas the space 8 communicates at its upper por- I tion with the drilling or boring column, and at its lower part with a central bore 10 disposed in the shaft 6 of the turbine.
  • the bore 10 terminates at its other end in a zone situated in immediate proximity to the drilling tool 1 for reasons discussed hereafter.
  • the internal face of the reservoir 7 delimiting the cylindrical space 8 consists of a wall 1 1 which is deformable in response to a pressure differential and the reservoir 7 is filled with a gas having a specific pressure.
  • FIG. 2 schematically illustrates the regulating device of FIG. 1, on an enlarged scale.
  • the hydraulic fluid or drilling mud which actuates the turbine 2 flows at a constant rate of flow Q from the drilling column 4.
  • the largest portion of this fluid is transmitted through the annular space 9 to the inlet E of the turbine 2 at a pressure P and at a rate of flow Q
  • This fluid which circulates in the direction indicated by the arrows drawn in continuous lines, actuates the turbine 2 and follows an upward path in the annular space between the wall of the drilled well 12 and that of the drilling column 4 in the direction indicated by the arrows drawn in broken line in FIG.
  • FIGS. land 2 a portion of the fluid coming from the drilling column 4 is diverted through the cylindrical space 8 in the direction indicated by the arrows drawn in dashed line, and after passing through the bore 10 of the shaft 6, this fluid serves to irrigate the drilling tool 1 whose active parts are free from the drilled or excavated material.
  • this irrigating or washing effect of the tool is very important since it permits use of the drilling tool under optimum conditions so as to obtain a maximum speed of advance for the drilling tool.
  • the fluid flow Q diverted through the space 8 depends upon the cross section of the space 8 and therewith upon the deformation of the membrane 11 in response to the pressure differential acting upon each of the faces thereof.
  • the pressure P, inside the reservoir 7 has a specific value so that under the normal operation of the system, the cross section of the cylindrical space 8 provides a flow O, which is equal to Q Q Q being the total flow of fluid delivered by the drilling column, and Q, the flow of fluid at the inlet of the turbine at the desired operating condition.
  • the regulating device according to the present invention affords a number of significant advantages as compared to the prior art devices in which an excess flow of fluid is employed forthe regulation of the system operation. More particularly, the energy of the excess fluid which is not utilized for the drilling turbine is used for freeing the active parts of the tool from the drilling or excavating material. Additionally, the present regulating device is not very cumbersome and may be easily adapted to drilling turbines wherein the internal pressure drop decreases .with the speed of rotation. However, it should be noted that it is possible for one of ordinary skill in the art to modify the above-described device without departing from the spirit and scope of the present invention.
  • FIG. 3 illustrates another embodiment of the regulating device in accordance with the present invention for use in a slow drilling turbine whose pressure drop decreases with the speed of rotation of the turbine.
  • the regulating device is provided at the interior of the body 5 with a member of the type having variable orifices adapted to provide communication between the bore 10 of the shaft 6 of the rotor and the drilling column 4.
  • This member includes a fixed cylindrical sleeve 19 whose inner bore is in communication with the bore 10 of the shaft 6, the cylindrical sleeve being integrally connected with the body 5 by means of fastening or attaching arms 20' shown schematically, and a cylindrical sleeve 21 which is axially movable with respect to the axis of the body 5.
  • This sleeve is placed coaxially with respect to the sleeve 19 and has a slightly greater inside diameter than the outside diameter of the sleeve 19 such that it is axially slideable with respect to the latter.
  • the sleeve 21 which is closed at the upper part thereof carries an axle 22 supported by a bearing 23 that is integrally connected with the body 5, for example by means of supporting arms schematically shown at 24.
  • the axle 22 is prevented from rotating by means of-a key-groove assembly 25, which is schematically illustrated.
  • the upper part of the axle 22 is provided with a plate 26 and elastic means 27 are interposed between the plate 26 and the bearing 23.
  • these elastic means may, for example, consist of a deformable elastic sleeve operating by compression as illustrated. However, it is understood that other elastic means may be used, for example a helical spring or the like.
  • the sleeves 19 and 21 are each provided with orifices in the walls thereof with the orifices provided in the sleeve 21 arranged for cooperation with those of the sleeve 19, as will be described hereinbelow.
  • the shape or configuration of these orifices is determined in accordance with the dimensions of the sleeves and the operating conditions.
  • FIG. 3 two types of orifices have been shown schematically for purposes of illustration only.
  • the orifices 28 have an elongated shape in a plane perpendicular to the axis of the device, whereas the orifices 28 are circular in shape and may be formed by a simple drilling operation.
  • the regulating device occupies the position shown in FIG. 3.
  • the orifices of the sleeve 21 partially uncover or expose the orifices of the sleeve 19, and a part of the drilling fluid is diverted toward the bore of the shaft 6, as indicated by the arrows F whereas the principal portion of the fluid flows toward the inlet of the turbine in the direction indicated by the arrow F which is supplied with a fluid flow Q,,.
  • Q designates the flow of fluid coming from the surface via the drilling column, this flow being constant, and Q, Q Q represents the flow of fluid diverted toward the bore of the shaft 6.
  • the sleeve 19 may be integrally connected with the shaft 6 of the turbine and be rotatably driven by thelatter with the orifices such as 28 being disposed in such a manner that, for a specific axial position of the movable sleeve 21, the uncovered or exposed cross section of the orifices provided in the sleeve 19 are independent of the rotation of this sleeve with respect to the sleeve 21 and independent of the speed rotation at which it is driven or carried along.
  • the orifices may also be disposed in such a manner that, with the sleeve 19 being rotatably driven by the shaft 10, the duration for which the orifices of the sleeve 19 are uncovered by the orifices of the sleeve 21 is proportional to the speed of rotation of the turbine, and the elastic means 27 may be employed either simultaneously or not employed at all in order to regulate the position of the sleeve 21.
  • FIG. 4 there is schematically illustrated another embodiment of the regulating device of the present invention which is adaptable for use with any type of turbines, and more particularly for turbines whose internal pressure drop is independent of the operation thereof, such as turbines with normal bladings.
  • the hollow axle 6 of the rotor of the drilling turbine 2 is extended into the body 5 of the regulating device 3.
  • the upper end of the axle 6 is closed by a stopper member or plug 13 integrally connected with the shaft 6, for example by a threaded connection.
  • the plug is provided with a ring or crown 14 concentrically arranged with respect to the shaft 6 of the turbine 2.
  • the lateral wall of the shaft 6 situated at the interior of the body 5 is provided with orifices 15 for communication between the bore 10 of the shaft 6 and the interior space of the body 5.
  • Deformable flexible resilient elements such as laminae 16 are secured to the shaft 6 and which, in the absence of rotation of the shaft 6, obstruct the orifices as shown in the left portion of FIG. 4. These elements are secured at one end thereof, for example at the lower end, by any conventional means such as screws, a clamping ring, or by welding, as schematically indicated at 17.
  • the length of the elements 16 is such that the free ends thereof which are herein illustrated as their upper ends are movable within the annular space between the shaft 6 and the crown 14.
  • the elements 16 are provided with flyweights-18 at the free ends thereof which serve for making the elements responsive to the speed of rotation of the shaft 6 as discussed below.
  • flyweights-18 When the turbine is stopped, the elements 16 occupy the position represented in the left portion of the figure, thus obstructing all of the orifices 15. In this case, all the hydraulic fluid passes into the annular space between the body 5 and shaft 6 and is thus utilized to start the turbine.
  • the centrifugal force exerted by the rotation of the shaft on the weights 18 causes the elastic elements 16 to be deformed as shown in the right portion of FIG. 4, thus partially and progressively uncovering the orifices' 15 through which the excess fluid flows so as to irrigate the drilling tool and the face of the cut.
  • the crown 14 serves as a stop to limit the deformation of the elastic elements 16 in order to avoid the deterioration thereof in case of extremely high speed rotation of the turbine.
  • the supply of fluid for the turbine is automatically adjusted to the desired value as function of the actual system operation of the turbine.
  • the cross sections and shapes of the orifices 15 and of the elements 16 as well as the elasticity of the latter, and the values of the masses of the weights 18 are chosen in accordance with the desired function of the system operation of the turbine.
  • FIG. schematically illustrates another embodiment of the regulating device, wherein a plurality of elastic elements 29 is utilized.
  • one end of the elements is secured to the shaft 6 of the turbine, or to a ring 31 integrally connected with the shaft and the other end thereof is secured to a ring 32 which is adapted to slide along a rod 33 integrally connected, for example, with the body 5, the connection not being shown.
  • the elements 29 are disposed in the manner of the faces of a prism such that, in the absence of rotation of the shaft 6,.each element is in contact with the adjacent element in order to define a prismatic volume having a polygonal essentially fluidtight base. Secured to each element is a weight 30 such that during the normal system operation or functioning of the turbine the centrifugal force exerted on the weights 30 deform the elements 29, as shown in FIG. 5, by driving or carrying the ring 32 downwardly.
  • FIG. 5B which is a crosssec tional view with regard to FIG.
  • the elements 29 are no longer in contact and a part 0 of the flow of fluid will proceed toward the bore of the shaft 6, as indicated by the arrow F
  • the speed of rotation of the turbine decreases, causing in that case a decrease of the centrifugal force.
  • the elements then approach the position illustrated in FIG. 5A corresponding to a zero speed of rotation of the shaft 6. In this manner, the flow Q decreases, entailing a corresponding increase of the flow of fluid Q.) for the turbine.
  • the deformation of the elements due to the action of the centrifugal force increases causing an increased separation of the elements 29, as shown, for example, in FIG. 5C.-The result thereof is an increase of the flow Q producing a corresponding reduction of the flow of fluid for the turbine.
  • the deformation of the elements may be limited by limiting'the sliding movement of the ring 32 in the downward direction by means of a shoulder portion 34 of the rod 33 which supports the ring for a maximal predetermined speed.
  • first communicating means directly connecting the source of fluid with an inlet of the turbine
  • second communicating means for communicating between the inlet of the turbine and the duct means at the upper end thereof
  • said second communicating means including at least one orifice having a variable cross section, the cross section being variable in accordance with a function of the pressure of the hydraulic fluid at the inlet of the turbine for permitting irrigation of the tool by a portion of the flow of the hydraulic fluid
  • said first communicating means being a rigid cylindrical body having one end connected with said turbine and having the other end connected with the source of fluid
  • said second communicating means including an annular reservoir concentrically positioned within said body, said reservoir having a rigid external wall and a deformable internal wall, said external wall and said body defining therebetween a first space through which hydraulic fluid flows from the source of fluid toward the inlet of the turbine, said internal wall of said reservoir defining said orifice through which the fluid flows from said first space toward the bore of said shaft, said internal wall of said reservoir being formed of a resilient material being deform
  • a device further comprising second duct means connecting said reservoir to a surface installation for the continuous regulation of the pressure within said reservoir.
  • a device for automatically regulating the system operation of a hydraulic turbine having an internal pressure drop which decreases with the speed of rotation, wherein the turbine drives a tool, and hydraulic fluid is supplied at an essentially constant rate of flow from a source of fluid comprising in combination a first duct means in the form of a bore-provided in a shaft of the turbine and having a lower part thereof terminating in the immediate vicinity of the tool, first communicating means directly connecting the source of fluid with an inlet of the turbine, second communicating means for communicating between the inlet of the turbine and the first duct means at an upper end thereof, said second communicating means including at least one orifice having a variable cross section which is variable in accordance with a function of the pressure of the hydraulic fluid at the inlet of the turbine for permitting irrigation of the tool by a portion of the flow of the hydraulic fluid, said first communication means being a rigid cylindrical body having one end connected with said turbine and having the other end connected with the source of fluid, said second communicating means including a first cylindrical sleeve coaxially positioned with respect to
  • said resilient means is in the form of a helical spring having one end secured to said second sleeve and'the other secured to said cylindrical body.
  • said resilient means is in the form of a tubular element being elastically deformable by a compression force, said element being supported between a shoulder portion of said second sleeve and a shoulder portion of said cylindrical body.
  • a device wherein said first sleeve is integrally connected for rotation with the shaft of said turbine.
  • a device for automatically regulating the system operation of a hydraulic turbine wherein the turbine drives a tool and hydraulic fluid is supplied at an essentially constant rate of flow from a source of fluid
  • the device comprising in combination first duct means in the form of a bore provided in the shaft of the turbine and having the lower part thereof terminating in the immediate vicinity of the tool, first communicating means directly connecting the source of fluid with an inlet of the turbine, second communicating means for communication between the inlet of the turbine and an upper end of the first duct means, said second communicating means including at least one orifice having a variable cross section, the cross section being variable in accordance with a function of the speed of rotation of the shaft of the turbine for permitting irrigation of the tool by a portion of the flow of the hydraulic fluid, said first communicating means being a rigid cylindrical body having one end connected with said turbine and having the other end connected with the source of fluid, the second communicating means including the bored shaft of the turbine, said at least one orifice being provided in the lateral wall of the shaft and in the region of said body, and at least one deform
  • a device for automatically regulating the system operation of a hydraulic turbine wherein the turbine drives a tool and hydraulic fluid is supplied at an essentially constant rate of flow from a source of fluid
  • the device comprising in combination duct means in the form of a bore provided in the shaft of the turbine and having the lower part thereof terminating in the immediate vicinity of the tool, first communicating means directly connecting the source of fluid with an inlet of the turbine, second communicating means for communication between the inlet of the turbine and an upper end of the duct means, said second communicating means including at least one orifice having a variable cross section, the cross section being variable in accordance with a function of the speed of rotation of the shaft of the turbine for permitting irrigation of the tool by a portion of the flow of the hydraulic fluid, said first communicating means being a rigid cylindrical body having one end connected with said turbine and having the other end connected with the source of fluid, said second communicating means including a plurality of elastic elements connected with the shaft of the turbine and forming an essentially fluid-tight prism in the absence of rotation of said shaft, said elements being deformed
  • a device for automatically regulating the system operation of a hydraulic turbine wherein the turbine drives a tool and hydraulic fluid is supplied at an essentially constant rate of flow from a source of fluid
  • the device comprising in combination duct means in the form of a bore provided in the shaft of the turbine and having the lower part thereof terminating in the immediate vicinity of the tool, first communicating means directly connecting the source of fluid with an inlet of the turbine, second communicating means for communication between the inlet of the turbine and an upper end of the duct means, said second communicating means including at least one orifice having a variable cross section, the cross section being variable in accordance with a function of the speed of rotation of the shaft of the turbine for permitting irrigation of the tool by a portion of the flow of the hydraulic fluid, said first communicating means being a rigid cylindrical body having one end connected with said turbine and having the other end connected with the source of fluid, said second communicating means including a first cylindrical sleeve connected with the shaft of the turbine and communicating with the bore of said shaft, a second cylindrical sleeve closed at the upper part thereof

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  • Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Geology (AREA)
  • Mining & Mineral Resources (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Environmental & Geological Engineering (AREA)
  • Fluid Mechanics (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Geochemistry & Mineralogy (AREA)
  • Earth Drilling (AREA)
  • Details Of Spanners, Wrenches, And Screw Drivers And Accessories (AREA)
US00269733A 1971-07-07 1972-07-07 Device for automatically regulating the operation of a drilling turbine Expired - Lifetime US3802515A (en)

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FR7124949A FR2145060A5 (enrdf_load_stackoverflow) 1971-07-07 1971-07-07

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FR (1) FR2145060A5 (enrdf_load_stackoverflow)
NL (1) NL7209470A (enrdf_load_stackoverflow)
SU (1) SU604506A3 (enrdf_load_stackoverflow)

Cited By (30)

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US3964558A (en) * 1974-11-13 1976-06-22 Texas Dynamatics, Inc. Fluid actuated downhole drilling device
US4225000A (en) * 1978-09-11 1980-09-30 Maurer Engineering Inc. Down hole drilling motor with pressure balanced bearing seals
FR2458670A1 (fr) * 1979-06-13 1981-01-02 Foraflex Dispositif de carottage a la turbine avec tube suiveur
US4275795A (en) * 1979-03-23 1981-06-30 Baker International Corporation Fluid pressure actuated by-pass and relief valve
US4291723A (en) * 1979-03-23 1981-09-29 Baker International Corporation Fluid pressure actuated by-pass and relief valve
US4339007A (en) * 1980-07-25 1982-07-13 Oncor Corporation Progressing cavity motor governing system
US4396071A (en) * 1981-07-06 1983-08-02 Dresser Industries, Inc. Mud by-pass regulator apparatus for measurement while drilling system
US4498784A (en) * 1979-10-26 1985-02-12 Bernhardsson Goeran Method and a device for mixing and homogenization of a main substance with at least one additive substance, liquids in particular
US4543038A (en) * 1982-03-08 1985-09-24 The Garrett Corporation Sealing apparatus and method and machinery utilizing same
US4553611A (en) * 1984-04-20 1985-11-19 Lyons William C Pressure drop regulator for downhole turbine
WO1987006300A1 (en) * 1986-04-11 1987-10-22 Drilex Uk Limited Improvements in drilling using downhole drilling tools
US4768598A (en) * 1987-10-01 1988-09-06 Baker Hughes Incorporated Fluid pressure actuated bypass and pressure indicating relief valve
WO1988006676A1 (en) * 1987-03-02 1988-09-07 Davis Lynn M Speed governed rotary device
US6263969B1 (en) 1998-08-13 2001-07-24 Baker Hughes Incorporated Bypass sub
WO2002046565A3 (en) * 2000-12-04 2002-10-24 Rotech Holdings Ltd Speed governor
US20040108138A1 (en) * 2002-08-21 2004-06-10 Iain Cooper Hydraulic Optimization of Drilling Fluids in Borehole Drilling
US20050109541A1 (en) * 2003-11-17 2005-05-26 Marvin Mark H. Low friction face sealed reaction turbine rotors
US20050173157A1 (en) * 2004-02-05 2005-08-11 Bj Services Company Flow control valve
US20050211471A1 (en) * 2004-03-29 2005-09-29 Cdx Gas, Llc System and method for controlling drill motor rotational speed
US20060124362A1 (en) * 2004-11-17 2006-06-15 Tempress Technologies, Inc. Floating head reaction turbine rotor with improved jet quality
US20100307833A1 (en) * 2009-06-08 2010-12-09 Tempress Technologies, Inc. Jet turbodrill
US20110036376A1 (en) * 2009-08-13 2011-02-17 Wojciechowski Iii Donald Anthony Rotating fluid nozzle for tube cleaning system
US8528649B2 (en) 2010-11-30 2013-09-10 Tempress Technologies, Inc. Hydraulic pulse valve with improved pulse control
US20150068763A1 (en) * 2012-04-03 2015-03-12 Cff Technologies Limited Downhole actuator
US20150300129A1 (en) * 2012-12-11 2015-10-22 Welltec A/S Downhole power system
US9249642B2 (en) 2010-11-30 2016-02-02 Tempress Technologies, Inc. Extended reach placement of wellbore completions
US9279300B2 (en) 2010-11-30 2016-03-08 Tempress Technologies, Inc. Split ring shift control for hydraulic pulse valve
US9399230B2 (en) 2014-01-16 2016-07-26 Nlb Corp. Rotating fluid nozzle for tube cleaning system
US10590709B2 (en) 2017-07-18 2020-03-17 Reme Technologies Llc Downhole oscillation apparatus
US10871063B2 (en) 2014-12-29 2020-12-22 Halliburton Energy Services, Inc. Toolface control with pulse width modulation

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Cited By (47)

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US3964558A (en) * 1974-11-13 1976-06-22 Texas Dynamatics, Inc. Fluid actuated downhole drilling device
US4225000A (en) * 1978-09-11 1980-09-30 Maurer Engineering Inc. Down hole drilling motor with pressure balanced bearing seals
US4275795A (en) * 1979-03-23 1981-06-30 Baker International Corporation Fluid pressure actuated by-pass and relief valve
US4291723A (en) * 1979-03-23 1981-09-29 Baker International Corporation Fluid pressure actuated by-pass and relief valve
FR2458670A1 (fr) * 1979-06-13 1981-01-02 Foraflex Dispositif de carottage a la turbine avec tube suiveur
US4343370A (en) * 1979-06-13 1982-08-10 Commissariat A L'energie Atomique Turbo-coring device equipped with a following pipe
US4498784A (en) * 1979-10-26 1985-02-12 Bernhardsson Goeran Method and a device for mixing and homogenization of a main substance with at least one additive substance, liquids in particular
US4339007A (en) * 1980-07-25 1982-07-13 Oncor Corporation Progressing cavity motor governing system
US4396071A (en) * 1981-07-06 1983-08-02 Dresser Industries, Inc. Mud by-pass regulator apparatus for measurement while drilling system
EP0069530A3 (en) * 1981-07-06 1985-07-31 Dresser Industries,Inc. Mud by-pass regulator apparatus for measurement while drilling system
US4543038A (en) * 1982-03-08 1985-09-24 The Garrett Corporation Sealing apparatus and method and machinery utilizing same
US4553611A (en) * 1984-04-20 1985-11-19 Lyons William C Pressure drop regulator for downhole turbine
WO1987006300A1 (en) * 1986-04-11 1987-10-22 Drilex Uk Limited Improvements in drilling using downhole drilling tools
US4775017A (en) * 1986-04-11 1988-10-04 Drilex Uk Limited Drilling using downhole drilling tools
WO1988006676A1 (en) * 1987-03-02 1988-09-07 Davis Lynn M Speed governed rotary device
US4776752A (en) * 1987-03-02 1988-10-11 Davis Lynn M Speed governed rotary device
US4768598A (en) * 1987-10-01 1988-09-06 Baker Hughes Incorporated Fluid pressure actuated bypass and pressure indicating relief valve
US6263969B1 (en) 1998-08-13 2001-07-24 Baker Hughes Incorporated Bypass sub
WO2002046565A3 (en) * 2000-12-04 2002-10-24 Rotech Holdings Ltd Speed governor
US6854953B2 (en) 2000-12-04 2005-02-15 Rotech Holdings, Limited Speed governor
US20040108138A1 (en) * 2002-08-21 2004-06-10 Iain Cooper Hydraulic Optimization of Drilling Fluids in Borehole Drilling
EP1398456A3 (en) * 2002-08-21 2005-03-23 ReedHycalog UK Limited Hydraulic optimization of drilling fluids in borehole drilling
US20050109541A1 (en) * 2003-11-17 2005-05-26 Marvin Mark H. Low friction face sealed reaction turbine rotors
US7201238B2 (en) 2003-11-17 2007-04-10 Tempress Technologies, Inc. Low friction face sealed reaction turbine rotors
US7086486B2 (en) 2004-02-05 2006-08-08 Bj Services Company Flow control valve and method of controlling rotation in a downhole tool
GB2411186A (en) * 2004-02-05 2005-08-24 Bj Services Co Well cleaning flow control valve
US20050173157A1 (en) * 2004-02-05 2005-08-11 Bj Services Company Flow control valve
GB2411186B (en) * 2004-02-05 2006-10-04 Bj Services Co Flow control valve
WO2005100731A1 (en) * 2004-03-29 2005-10-27 Cdx Gas, Llc System and method for controlling drill motor rotational speed
US20050211471A1 (en) * 2004-03-29 2005-09-29 Cdx Gas, Llc System and method for controlling drill motor rotational speed
US20060124362A1 (en) * 2004-11-17 2006-06-15 Tempress Technologies, Inc. Floating head reaction turbine rotor with improved jet quality
US7198456B2 (en) 2004-11-17 2007-04-03 Tempress Technologies, Inc. Floating head reaction turbine rotor with improved jet quality
US8607896B2 (en) 2009-06-08 2013-12-17 Tempress Technologies, Inc. Jet turbodrill
US20100307833A1 (en) * 2009-06-08 2010-12-09 Tempress Technologies, Inc. Jet turbodrill
US20110036376A1 (en) * 2009-08-13 2011-02-17 Wojciechowski Iii Donald Anthony Rotating fluid nozzle for tube cleaning system
US8298349B2 (en) 2009-08-13 2012-10-30 Nlb Corp. Rotating fluid nozzle for tube cleaning system
US8528649B2 (en) 2010-11-30 2013-09-10 Tempress Technologies, Inc. Hydraulic pulse valve with improved pulse control
US8939217B2 (en) 2010-11-30 2015-01-27 Tempress Technologies, Inc. Hydraulic pulse valve with improved pulse control
US9249642B2 (en) 2010-11-30 2016-02-02 Tempress Technologies, Inc. Extended reach placement of wellbore completions
US9279300B2 (en) 2010-11-30 2016-03-08 Tempress Technologies, Inc. Split ring shift control for hydraulic pulse valve
US20150068763A1 (en) * 2012-04-03 2015-03-12 Cff Technologies Limited Downhole actuator
US9845662B2 (en) * 2012-04-03 2017-12-19 Cff Technologies Limited Downhole actuator
US10472930B2 (en) 2012-04-03 2019-11-12 Cff Technologies Limited Downhole actuator
US20150300129A1 (en) * 2012-12-11 2015-10-22 Welltec A/S Downhole power system
US9399230B2 (en) 2014-01-16 2016-07-26 Nlb Corp. Rotating fluid nozzle for tube cleaning system
US10871063B2 (en) 2014-12-29 2020-12-22 Halliburton Energy Services, Inc. Toolface control with pulse width modulation
US10590709B2 (en) 2017-07-18 2020-03-17 Reme Technologies Llc Downhole oscillation apparatus

Also Published As

Publication number Publication date
SU604506A3 (ru) 1978-04-25
NL7209470A (enrdf_load_stackoverflow) 1973-01-09
FR2145060A5 (enrdf_load_stackoverflow) 1973-02-16

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