RU2732322C1 - Oscillator for a drill string - Google Patents

Abstract

FIELD: soil or rock drilling.

SUBSTANCE: invention relates to hydraulic rotary drilling drives located in wells, in particular to oscillators for a drill string, designed to create hydromechanical impulses acting on a drill string. Oscillator comprises a gerotor screw hydraulic motor, a valve, a plunger module, a transmission shaft, a radial-thrust rotation support, a hydromechanical pulse generator and a spring module. Valve comprises movable valve element and fixed valve element. Movable valve element is equipped with installed in it first valve plate and is movable relative to fixed valve element. Fixed valve element is equipped with the second valve plate installed in it, forms with it a valve hole and has a longitudinal axis. In operation, the valve elements interact to form an alternating fluid flow passage through the valve. Movable valve element is equipped with a tubular shank, which inner cavity is made with possibility to communicate with flow of fluid medium and formation of flow channel through inner cavity of tubular shank. First valve plate is made in the form of the first throttling sleeve with a flow channel fixed to the plunger module. Second valve plate is made in the form of the second throttling sleeve with flow channel attached to the housing. Throttle bushing of fixed valve element is located adjacent to generator of hydromechanical pulses. Internal profile of flow channel of throttle sleeve of fixed valve element is confuser downstream. Plunger module is placed at the inlet of the gerotor screw hydraulic motor and is attached to the inlet part of the rotor of the gerotor screw hydraulic engine. Movable valve element is made in the form of a throttling sleeve with a flow channel attached to the plunger module, the internal profile of which is diffuser downstream. Central longitudinal axis of flow channel installed in plunger module of throttle bushing is shifted relative to central longitudinal axis of rotor of gerotor screw hydraulic engine, its maximum displacement relative to the central longitudinal axis of the rotor of the gerotor screw hydraulic engine is equal to the eccentricity of the central longitudinal axis of the rotor of the gerotor screw hydraulic motor relative to the central longitudinal axis of the elastomer plate in the stator. Radial-thrust support of rotation is arranged in output part of oscillator, and transmission shaft is arranged between output part of rotor of gerotor screw hydraulic engine and inlet part of hollow shaft of radial-thrust rotation support and is attached by one edge to the rotor output of the gerotor screw hydraulic engine, and by the other edge to the shaft radial thrust bearing shaft inlet part.

EFFECT: longer service life and reliability of the oscillator, reduced friction forces of the drill string on the well wall, reduced torsional stresses in the drill string, increased resource of the bit and increased rate of drilling when drilling inclined and horizontal wells.

1 cl, 11 dwg

Description

The invention relates to hydraulic drives for rotary drilling, placed in wells, in particular to oscillators for a drill string, designed to create hydromechanical impulses acting on the drill string.

Known downhole tool for cleaning a cased section of a well, comprising a housing, an inlet for fluid through which fluid can enter the housing, and a plurality of outlets through which fluid can exit the housing and act on the material of the wellbore wall, as well as a valve arrangement for selective regulating the volume of fluid directed from the outlet between at least one of the outlets and at least one other outlet, while with the arrangement of valves in the first configuration, a larger volume of fluid is directed from the inlet to the specified at least at least one of the outlets, and a smaller volume of fluid is directed from the inlet to the specified at least one other outlet, and with the arrangement of valves in the second configuration, a smaller volume of fluid is directed from the inner cavity to the specified at least one from the outlets and a larger volume of fluid is directed from the inlet one hole into the specified at least one more other outlet (US 8251144 B2, 28.08.2012).

The disadvantage of the known design is the incomplete possibility of its use in the bottom hole assembly (BHA) to create hydromechanical impulses with a given frequency and amplitude of oscillations to reduce the friction forces of the drill string against the borehole walls, reduce torsional stresses in the drill string during rotary drilling (with rotation of the drill string ) of inclined and horizontal wells using a gerotor screw hydraulic motor, as well as to prevent sticking of the drill string caused by a pressure drop, which is explained by the lack of an outlet flow path necessary to supply drilling fluid under pressure to the BHA to drive the rotor of the gerotor screw hydraulic motor with a bit.

The disadvantage of the known design is also the placement of a stop at the inlet with holes in the transverse wall, while solid abrasive particles of the drilling mud, for example, up to 2% sand with dimensions of 0.15 ÷ 0.95 mm and up to 5% oil products of polymer-clay drilling mud with a density 1.16 ÷ 1.26 g / cm ³ pumped at a hydrostatic pressure, for example, 25 ÷ 35 MPa, cause sludge and increase pressure losses when the drilling fluid passes through the stop with holes in the transverse wall, as a result of which the required mechanical power of the shock is not provided tool and vibration amplitude of the drill string.

The disadvantage of the known design is also the rigid fixation of the oscillating plate 34 made of hard alloy (tungsten carbide) in the valve element 22, which defines the main longitudinal axis 20, and is rigidly threaded with the rotor 52, as a result of this, the service life of the plates made of hard alloy is not ensured, the main defects are known structures - chipping, chipping and destruction of sliding contact rectangular ends of the oscillating valve plate 34 and the stationary valve plate 24, also made of hard alloy, is shown in FIG. 2.

Known downhole impulse device in combination with a drill string, including tubing, a drilling motor consisting of a stator connected to the tubing, and a rotor fixed in the stator so as to rotate relative to the stator and tubing under the influence flow of drilling fluid under pressure in the tubing, a drill bit connected to the lower end of the rotor of the drilling motor in such a way as to rotate with the rotor of the drilling motor, and a rotor retainer, a downhole impulse device including a tubular body connected to the tubing, a body having an axial bore extending along the axis to allow the passage of drilling fluid therethrough, a valve located in the bore of the tubular body and determining the size of the section for the flow of drilling fluid, a valve consisting of a stationary part, stationary relative to the tubular body, and rotating a rotating part, movably located in the tubular body so as to vary the flow area due to rotation of the rotating part relative to the stationary part, as well as a drive link located between the rotating part of the valve and the rotor of the drilling motor, so as to rotate the rotating part of the valve relative to the tubing pipes together with the rotor of the drilling motor, while the rotor retainer includes an annular locking element mounted in series with the tubing between the stator housing of the drilling motor and the tubular housing of the impulse device and the locking element passing through the locking element so as to be connected between the rotor of the drilling motor and a drive link, as well as a fixing element, including an enlarged part above the stopper element, which cannot pass through the annular stopper element (US 8181719 B2, 22.05.2012).

The disadvantage of the known design is the increasing longitudinal play of the plunger 80 during operation, as well as the need to adjust the flow section 64 in the position when the channels 70 of the plunger 80 are overlapped using the threaded bushing 48 and screws 52, while the plunger 80 is held in the longitudinal direction by the cardan shaft 72, an adapter 32, by the rotor 20 of the screw gerotor motor, the spindle assembly fastened to the bit 22, and determines the value of the longitudinal play of the plunger 80, the slotted conical channel 64 and the flow rate of the drilling fluid through the sections 64, is shown in FIG. 4, 6, 8.

As a consequence, as the known downhole impulse device is developed in the drill string assembly, the energy characteristics of the fluid pressure pulses directed against the flow towards the percussion tool are reduced, and the mechanical power of the percussion tool required to reduce the friction forces of the drill string against the borehole walls is not provided. , reduction of torsional stresses in the drill string when drilling horizontal wells, as well as to prevent sticking of the drill string.

Another disadvantage of the known design is an increase in the likelihood of hydroabrasive erosion of the slotted conical channel 64, which is explained by the fact that solid abrasive particles of the drilling mud, for example, up to 2% sand with sizes of 0.15 ÷ 0.95 mm and up to 5% of oil products polymer - clay drilling solution with a density of 1.16 ÷ 1.26 g / cm ³ pumped at a hydrostatic pressure, for example, 25 ÷ 40 MPa, when the plunger 80 is exposed to the force from the bit 22, directed from the bottom of the well to the downhole impulse device, transmitted through the rotor 20 of the volumetric engine, adapter 32, and propeller shaft 72, increase the wear of the joints and the longitudinal play of the plunger 80, as a result of which the flow area of the slotted conical channel 64 decreases, the flow rate of the drilling fluid through the slotted conical channel 64 increases, the required mechanical power of the percussion tool and the vibration amplitude are not provided drill string to reduce friction forces of the drill string against the borehole wall ...

Known impulse flow device to provide a shock effect, containing a housing for installation in a column, the housing has a through hole to allow the passage of liquid through it, a valve located in the hole to provide a flow passage, including a valve component that is movable in order to varying the area of flow of a fluid to alter the flow of a fluid through it, as well as a hydraulically driven downhole motor functionally associated with a valve to drive a valve component and a pressure sensing device that expands or contracts in response to pressure changes fluid created by changing the fluid flow, while the contraction and expansion of the pressure-sensitive device provides a shock effect (US 6279670 B1, 28.08.2001).

The disadvantage of the known design is its complexity and high cost, as well as the fact that the impulse force is used mainly to create the effect of percussion drilling on the bit, as a result of which the technological possibilities of using the bottom hole assembly (BHA) for generating hydromechanical impulses with a given frequency and amplitude are reduced. vibrations acting on the string to reduce the frictional forces of the rotating drill string against the borehole wall, reduce torsional stresses in the drill string when drilling horizontal wells, and also to prevent sticking of the drill string.

The disadvantage of the known design is also the placement of a consumable insert 14 at the engine inlet (shown in Fig. 2), while solid abrasive particles of the drilling fluid, for example, up to 2% sand with dimensions of 0.15 ÷ 0.95 mm and up to 5% oil products polymer - clay drilling mud with a density of 1.16 + ÷ 1.26 g / cm ³ pumped at hydrostatic pressure, for example, 25 ÷ 35 MPa, lead to mud sloughing in the flow insert 14, which overlaps the trajectory of the drilling mud flow, and to pressure losses when passing through the holes of the insert 14, as a result of which hydraulic shocks occur in the drill string, the energy characteristics of the pulsating fluid pressure directed towards the percussion tool 3 (US 6588518 B2, Jul. 8,2003), which is sensitive to pressure for creating an impulse force on the section of the drill string, where the impulse force is used only to create the effect of hammer drilling on the bit.

Known shock-rotary device containing a housing adapted for mounting on a support element, a positive displacement motor having a stator and a rotor, in which, during operation, the rotor oscillates, rotating and moving in the transverse direction inside the stator, and a valve including an oscillating first valve element and a stationary a second valve element, where each valve element forms a valve opening and has a main longitudinal axis, the first valve element is connected to the rotor and is movable relative to the second valve element, while in operation the valve elements interact, together forming a variable flow area through the valve, and, at least one of the openings of the valve elements is offset from the corresponding main longitudinal axis (RU 2362866 C2, 27.07.2009).

During operation, the pressure drop of the drilling fluid through the screw gerotor hydraulic motor 19 shifts the rotor 24 towards the valve device 30, this force is prevented by the valve device 30 controlled (rotated) by the rotor 24 of the engine 19, while the pressure drop can be through the motor 19 in the opposite direction and can move the rotor 24 towards the stop 32 with a transverse wall located at the engine inlet, as a result of which the rotor 24 itself is a source of alternating axial shock loads.

The disadvantage of the known design is the rigid fixation of the oscillating plate 34 made of hard alloy (tungsten carbide) in the valve element 38, which defines the main longitudinal axis A, and is rigidly threaded 42 with the rotor 24, as a result of this, the resource is not provided, while the main defects of the known design are chipping, chipping and fracture of sliding contact rectangular ends of the oscillating plate 34 and the stationary valve plate 36, also made of hard alloy, is shown in FIG. 3.5.

Another disadvantage of the known design is the placement of a stop 32 with holes 19 in the transverse wall at the engine inlet, while solid abrasive particles of the drilling mud, for example, up to 2% sand with dimensions of 0.15 ÷ 0.95 mm and up to 5% of oil products polymer - clay drilling mud with a density of 1.16-1.26 g / cm ³ , pumped at a hydrostatic pressure, for example, 25 ÷ 35 MPa, lead to mud sloughing on the transverse wall of the stop 32, which overlaps the trajectory of the drilling mud flow, as well as to losses pressure when passing through the holes of the stop 32, as a result of which hydraulic shocks occur in the drill string, the required mechanical power of the percussion tool and the vibration amplitude of the drill string are not provided to reduce the friction forces of the drill string against the borehole wall, reduce torsional stresses in the drill string when drilling horizontal wells, and to prevent sticking of the drill string.

Known oscillator for a drill string, containing a gerotor screw hydraulic motor, including a stator with an elastomer lining fixed in it with internal helical teeth and a rotor with external helical teeth located inside the stator, the rotation of the rotor is carried out by pumping a fluid medium, the number of rotor teeth is one less than the number teeth of the elastomer lining, the strokes of the helical teeth of the elastomer lining and the rotor are proportional to their number of teeth, the central longitudinal axes of the rotor and the elastomer lining are offset from each other by the amount of eccentricity, and the valve including the first valve element and the stationary second valve element, the first valve element is equipped with the first valve plate, the second valve element is provided with a second valve plate installed therein, and the second valve element with the second valve plate installed therein forms a valve hole and has a main longitudinal axis, the first valve element is fastened with the rotor and has the ability to move relative to the second valve element, while in operation the valve elements interact, jointly forming a variable flow area for the fluid through the valve, while the oscillator contains a plunger module attached to the first valve element, the first valve plate is placed inside the plunger module with the possibility of longitudinal movement, and the plunger module is equipped with a spring device that loads the first valve plate for permanent contact with the second valve plate located in the second valve element, while the first valve plate located in the plunger module has a solid end for contact with the second valve plate , installed in the second valve element and forming a valve hole, and also contains a transmission shaft fastened to the inlet part of the rotor, an angular contact support of rotation, including a hollow shaft installed in the specified radial contact support of the rotary rotationally and fastened to the transmission shaft, and a hydromechanical impulse generator located upstream of the angular contact support of rotation, comprising a housing made of outer tubular elements, a mandrel placed inside the housing made of inner tubular elements telescopically interconnected , elements for transmitting torque between the body and the mandrel during longitudinal displacement relative to each other, these tubular elements are equipped with threads, and also containing a spring module between the body and the mandrel, a thrust sleeve between the upper thrust end of the body and the spring module, said outer tubular elements having located along the upper and lower stop ends on opposite edges of the spring module, the upper stop end of the first tubular element and the lower end of the second tubular element, simultaneously engaging and loading the spring module during longitudinal compression of the said tubular elements elements relative to each other, the upper abutment end of the second tubular element and the lower abutment end of the first tubular element, simultaneously engaging and loading the spring module when the said tubular elements are stretched relative to each other, an annular piston with seals on the outer and inner surfaces, installed between the inner surface of the housing and the outer surface of the mandrel, responsive to fluid pressure, and also containing seals in the upper part between the body and the mandrel and a chamber for the working fluid - oil, bounded by the seals in the upper part of the body and the seals of the annular piston between the body and the mandrel, and a thrust ring mounted on an inner tubular element constituting the lower part of the mandrel, while the rotary drive for transferring moment between the mandrel and the body during longitudinal movement relative to each other is equipped with an impact ring installed in the mandrel with the possibility of longitudinal movement of the mandrel ki with an impact ring inside the thrust sleeve (RU 2565316 C1, 20.10.2015).

The disadvantage of the known design is the incomplete possibility of increasing the resource and reliability due to the high activity of cavitation processes of the flow of a hydroabrasive medium, for example, a polymer - clay drilling mud, with a density of 1.16 ÷ 1.26 g / cm ³ , containing up to 2% sand with dimensions of 0.15 ÷ 0.95 mm and up to 10% of petroleum products pumped at hydrostatic pressure, for example, 20 ÷ 35 MPa, which is explained by intense abrasive and erosive wear (erosion) of the plunger module 23, rigidly fastened to the valve element 14 using a common thread 24, and also the valve plate 16 made of hard alloy, placed in the plunger 27, installed in the hole 28 of the plunger module 23 with the possibility of telescopic movement along its own central longitudinal axis 29, as well as slashing and gripping the spring device 30, fixed by the nut 31, loading the plunger 27 with her valve plate 16, having a solid end 33 for contact with the end 34 valve plate 17 installed in the valve element 15 and forming the valve hole 18, together forming a variable flow area 22 for the fluid 7 through the valve 13.

In the known design, the flow of fluid 7 is directed through the drill pipe string, which contains the oscillator, into the valve 13 outside, from the cavity inside the oscillator, enclosing the plunger module 23, into the gap between the end face 33 of the valve plate 16 and the end face 34 of the valve plate 17, the valve plate 16, located in the plunger 27 inside the plunger module 23, has a solid end 33 for contact with the end 34 of the valve plate 17 installed in the valve element 15 and forming the valve hole 18, together forming a variable flow area 22 for the fluid 7 - drilling mud through valve 13, as a result of this, the known design has a drawback: metal particles (shavings and scale) that have passed through the drill string filter are decelerated and muddied at the end of the stationary valve element 15 and at the end 34 of the valve plate 17 installed in the valve element 15, as a result prevents the possibility of ingress of abrasive hours particles passing through the drill string filter between the contacting ends 33 and 34 of the valve plates 16, 17, which disrupts the operation of the oscillator in the well.

Closest to the claimed invention is an oscillator for a drill string, containing a gerotor screw hydraulic motor, including a tubular stator with an elastomer lining with internal helical teeth fixed in it and a rotor with external helical teeth located inside the stator, the rotation of the rotor is carried out by pumping a fluid medium, number of the rotor teeth by one less than the number of teeth of the elastomer lining, the strokes of the helical teeth of the elastomer lining and rotor are proportional to their numbers of teeth, and the central longitudinal axes of the rotor and the elastomer lining in the stator are displaced between themselves by the eccentricity value, and the valve including the first valve element and a stationary second valve element, the first valve element is provided with a first valve plate installed therein, the second valve element is provided with a second valve plate installed therein, and the second valve element with a second valve plate installed therein forms a the valve element has a main longitudinal axis, the first valve element is attached to the rotor and has the ability to move relative to the second valve element, and during operation, the valve elements interact, jointly forming a variable flow area for the fluid through the valve, and also containing a plunger module located between the first valve element and valve pair, as well as containing a transmission shaft fastened to the inlet part of the rotor, an angular contact support of rotation, including a hollow shaft mounted in said angular contact support of rotation with the possibility of rotation and fastened to the transmission shaft, and a generator of hydromechanical impulses, located upstream of the angular contact support of rotation, containing a housing made of outer tubular elements, a mandrel located inside the housing, made of inner tubular elements telescopically interconnected, elements for transmitting torque between at the body and the mandrel during longitudinal movement relative to each other, these tubular elements are equipped with threads, and also containing a spring module between the body and the mandrel, a thrust sleeve between the upper thrust end of the case and the spring module, said outer tubular elements having upper and lower thrust ends on opposite edges of the spring module, the upper abutting end of the first tubular element and the lower end of the second tubular element, simultaneously engaging and loading the spring module during longitudinal compression of the said tubular elements relative to each other, the upper abutting end of the second tubular element and the lower abutting end of the first tubular element, simultaneously engaging and loading the spring module when these tubular elements are stretched relative to each other, an annular piston with seals on the outer and inner surfaces, installed between the inner surface of the housing and the outer surface a new mandrel, responsive to fluid pressure, and also containing seals in the upper part between the body and the mandrel and a chamber for working fluid - oil, bounded by seals in the upper part of the housing and seals of the annular piston between the body and the mandrel, and a thrust ring mounted on the inner a tubular element constituting the lower part of the mandrel, while the rotary drive for transferring moment between the mandrel and the body during longitudinal movement relative to each other is equipped with an impact ring installed in the mandrel with the possibility of longitudinal movement of the mandrel with an impact ring inside the thrust sleeve, while the first valve element, attached to the rotor, equipped with a tubular shank directed towards the valve, the inner cavity of the tubular shank of the first valve element is configured to communicate with the fluid flow at the outlet from the gerotor screw hydraulic motor and to form a flow channel through the inner cavity of the pipes stem to the valve, and the plunger module contains an elastomer lining fixed inside it and is mounted on the tubular shank of the first valve element with the possibility of rotation and longitudinal movement relative to the said tubular shank of the first valve element, while the first valve plate is made in the form of a throttle valve attached to the plunger module bushings with a flow channel, the inner profile of which is converging downstream, the maximum displacement of the central longitudinal axis of the flow channel of the throttle sleeve relative to the central longitudinal axis of the elastomer lining in the stator is equal to the double value of the eccentricity of the central longitudinal axis of the rotor relative to the central longitudinal axis of the elastomer lining in the stator, and the maximum displacement of the central longitudinal axis of the flow channel of the second stationary sleeve relative to the central longitudinal axis of the elastomer lining in the stator is equal to the value of the eccentricity of the center longitudinal axis of the rotor relative to the central longitudinal axis of the elastomer lining in the stator (RU 2645198 C1, 16.02.2018).

The disadvantage of the known oscillator is the incomplete possibility of increasing the energy characteristics of the pulsating pressure of the fluid, as well as the mechanical power of the hydromechanical pulse generator and the operating range of the frequency and amplitude of the drill string oscillations with lower pressure losses.

The disadvantages of the known design are explained by the fact that the valve, including the first valve element attached to the rotor, provided with a tubular shank directed towards the valve, the inner cavity of the tubular shank of the first valve element is configured to communicate with the fluid flow at the outlet of the gerotor screw hydraulic motor and form the flow channel through the inner cavity of the tubular shank, and the stationary valve element, which interact during operation, jointly forming a variable flow area for the fluid, is located in the output part of the oscillator, as a result of which the energy characteristics of the upstream pressure pulses of the fluid through the hollow shaft are reduced. thrust bearing of rotation and, further, through chambers moving along the flow, isolated from each other between the teeth of the rotor and the shell made of stator elastomer in the gerotor screw hydraulic motor towards the generator mechanical impulses, as a result of this, the mechanical power of the hydromechanical impulse generator is not provided, which is necessary to reduce the friction forces of the drill string against the borehole walls, reduce torsional stresses in the drill string when drilling inclined and horizontal wells, as well as to prevent sticking of the drill string, as a result, additional mechanical power (increased pressure of the pump on the rig) required to drive a gerotor screw hydraulic motor with a drill bit located downstream of the oscillator in the drill string.

The disadvantage of the known oscillator is also the incomplete possibility of increasing the resource and reliability due to the fact that it contains a transmission shaft 47, essentially a flexible torsion shaft 47, fastened to the input part 48 of the rotor 5 of the engine 1 and the output part of the hollow shaft 50 installed in the angular contact support 49 of rotation and fastened to the torsion shaft 47 by means of an adapter 51 designed to direct the flow of fluid 7 from the hollow shaft 50 to the inlet of the gerotor screw hydraulic motor 1, in which the rotation of the rotor 5 is carried out by pumping the fluid 7 to drive the valve 13 of the oscillator, shown in FIG. nineteen.

When pumping a fluid 7 (drilling mud), an axial load acts on the helical teeth of the rotor 5, directed downstream of the flow of the fluid 7, and the torsion shaft is acted upon by equivalent stresses (according to von Mises) from the tightening torque of the thread of the torsion shaft 47, a tensile load associated holding the rotor 5 in the longitudinal direction to relieve the valve 13 from longitudinal movements, and the shear force (eccentricity) of the rotor 5 with helical teeth, planetary rotating in the lining 3 of the elastomer, and transmitting torque to the torsion shaft 47.

In this case, the equivalent stresses (according to von Mises) from the tightening torque of the thread of the torsion shaft 47, as well as from the tensile load acting on the torsion shaft 47, associated with holding the rotor 5 in the longitudinal direction to unload the valve 13 from longitudinal displacements and skewing force (eccentricity) planetary The rotor 5 with helical teeth rotating in the elastomer lining 3 does not provide the required values of the equivalent stresses in the critical zones, in essence, in the “threaded” grooves of the torsion shaft 47.

The technical problem to be solved by the invention is to increase the resource and reliability of the oscillator for the drill string, reduce the friction forces of the drill string against the borehole wall, reduce the torsional stresses in the drill string, increase the bit life and increase the ROP when drilling inclined and horizontal wells by increasing the energy characteristics of the pulsating pressure of the fluid and the mechanical power of the generator of hydromechanical impulses with a given frequency and amplitude of oscillations of the drill string at lower pressure losses due to the fact that the throttle sleeve of the stationary valve element fastened to the body is located adjacent downstream to the generator of hydromechanical impulses, the internal profile of the flow the channel of the stationary valve element fastened to the body of the throttle sleeve is made converging downstream, the plunger module, which includes an elastomer lining fixed inside it and installed thrown on the tubular shank of the movable valve element with the possibility of rotation and longitudinal movement relative to the tubular shank of the valve element, located at the inlet to the gerotor screw hydraulic motor and fastened to the inlet of the rotor of the gerotor screw hydraulic motor, the movable valve element is made in the form of a throttle sleeve fastened to the plunger module with a flow channel, the internal profile of which is made diffuser downstream, the central longitudinal axis of the flow channel installed in the said plunger module of the throttle sleeve is displaced relative to the central longitudinal axis of the rotor of the gerotor screw hydraulic motor, the angular contact support of rotation is located in the output part of the oscillator, and the transmission shaft placed between the outlet of the rotor of the gerotor screw hydraulic motor and the inlet of the hollow shaft of the angular contact support of rotation and is fastened with one edge to the outlet of the rotor g rotary screw hydraulic motor, and the other edge - with the input part of the shaft of the angular contact support of rotation.

The essence of the technical solution lies in the fact that in an oscillator for a drill string containing a gerotor screw hydraulic motor, including a tubular stator with an elastomer lining with internal helical teeth fixed in it and a rotor with external helical teeth located inside the stator, the rotor rotates by pumping fluid medium, the number of rotor teeth is one less than the number of teeth of the elastomer lining, the strokes of the helical teeth of the elastomer lining and the rotor are proportional to their number of teeth, and the central longitudinal axes of the rotor and elastomer lining in the stator are displaced between themselves by the amount of eccentricity, and a valve including a movable valve element and stationary valve element, the movable valve element is equipped with a first valve plate installed therein, the stationary valve element is equipped with a second valve plate installed therein, and the stationary valve element with a second valve plate installed therein th forms a valve opening and has a longitudinal axis, the movable valve element is movable relative to the stationary valve element, and during operation, the valve elements interact, jointly forming a variable flow area for the fluid through the valve, and also containing a plunger module in which the movable valve element is equipped tubular shank, the inner cavity of the tubular shank of the movable valve element is configured to communicate with the fluid flow and form a flow channel through the inner cavity of the tubular shank, and the plunger module contains an elastomer lining fixed inside it and is mounted on the tubular shank of the movable valve element with the possibility of rotation and longitudinal movement relative to the tubular shank of the movable valve element, while the first valve plate is made in the form of a first throttle bushing with a flow path fastened to the plunger module cash, and the second valve plate is made in the form of a second throttle sleeve fastened to the body with a flow channel, and also containing a transmission shaft, a radial-thrust support of rotation, including a hollow shaft installed in an angular contact support of rotation with the possibility of rotation, and a generator of hydromechanical impulses containing a housing made of outer tubular elements, a mandrel placed inside the casing made of inner tubular elements telescopically connected to each other, elements for transmitting a torque between the casing and the mandrel during longitudinal movement relative to each other, these tubular elements are equipped with threads, and containing a spring module between the housing and the mandrel, a thrust sleeve between the upper thrust end of the housing and the spring module, the said outer tubular elements having upper and lower thrust ends located along the opposite edges of the spring module, the upper thrust end of the first tubular th element and the lower end of the second tubular element, simultaneously engaging and loading the spring module during the longitudinal compression of these tubular elements relative to each other, the upper abutment end of the second tubular element and the lower abutment of the first tubular element, simultaneously engaging and loading the spring module when stretching the said tubular elements relative to each other, an annular piston with seals on the outer and inner surfaces, installed between the inner surface of the housing and the outer surface of the mandrel, responding to the pressure of the fluid medium, and also containing seals in the upper part between the housing and the mandrel and a chamber for the working fluid - oil, limited seals in the upper part of the body and seals of the annular piston between the body and the mandrel, and a thrust ring mounted on the inner tubular element constituting the lower part of the mandrel, while the drive for transferring the torque between the mandrel and the body with longitudinal movement relative to each other is equipped with an impact ring installed in the mandrel with the possibility of longitudinal movement of the mandrel with an impact ring inside the thrust sleeve, according to the invention, the throttle sleeve of the fixed valve element fastened to the body is located adjacent downstream to the generator of hydromechanical impulses, the inner profile of the flow channel fastened to the body of the throttle sleeve of the stationary valve element is made convergent downstream, the plunger module, including an elastomer lining fixed inside it and mounted on the tubular shank of the movable valve element with the possibility of rotation and longitudinal movement relative to the tubular shank of the valve element, is located at the inlet to the gerotor screw hydraulic motor and is fastened to the inlet part of the rotor of the gerotor screw hydraulic motor, while the movable valve element is made in the form of fastened to the plunger m with a throttle sleeve module with a flow channel, the internal profile of which is diffuser downstream, and the central longitudinal axis of the flow channel installed in the said plunger module of the throttle sleeve is displaced relative to the central longitudinal axis of the rotor of the gerotor screw hydraulic motor, and the maximum displacement of the central longitudinal axis of the flow channel installed in the plunger module of the throttle sleeve, the internal profile of which is made diffuser downstream, relative to the central longitudinal axis of the rotor of the gerotor screw hydraulic motor, is equal to the eccentricity of the central longitudinal axis of the rotor of the gerotor screw hydraulic motor relative to the central longitudinal axis of the elastomer lining in the stator, while radially the thrust bearing of rotation is located in the output part of the oscillator, and the transmission shaft is located between the output part of the rotor of the gerotor screw hydraulic motor and the input with one part of the hollow shaft of the angular contact support of rotation and is fastened with one edge to the outlet part of the rotor of the gerotor screw hydraulic motor, and the other edge - with the inlet part of the shaft of the angular contact support of rotation.

The maximum clearance between the end of the throttle sleeve, fastened to the plunger module of the movable valve element, and the end of the throttle sleeve, fastened to the body of the fixed valve element, is equal to the eccentricity of the central longitudinal axis of the tubular shank of the movable valve element relative to the central longitudinal axis of the rotor of the gerotor screw hydraulic motor.

Execution of the oscillator for the drill string in such a way that the throttle sleeve of the fixed valve element fastened to the body is located adjacent downstream to the generator of hydromechanical impulses, the internal profile of the flow channel fastened to the throttle sleeve body of the fixed valve element is converging downstream, the plunger module including the fixed inside it, an elastomer lining and mounted on the tubular shank of the movable valve element with the possibility of rotation and longitudinal movement relative to the tubular shank of the valve element, placed at the inlet to the gerotor screw hydraulic motor and fastened to the inlet part of the rotor of the gerotor screw hydraulic engine, while the movable valve element is made in the form of a throttle sleeve fastened to the plunger module with a flow channel, the internal profile of which is made as a diffuser downstream, and the central longitudinal axis of the flow about the channel installed in the said plunger module of the throttle sleeve is displaced relative to the central longitudinal axis of the rotor of the gerotor screw hydraulic engine, and the maximum displacement of the central longitudinal axis of the flow channel installed in the plunger module of the throttle sleeve, the internal profile of which is made diffuser downstream, relative to the central longitudinal axis of the gerotor rotor screw hydraulic motor, equal to the value of the eccentricity of the central longitudinal axis of the rotor of the gerotor screw hydraulic motor relative to the central longitudinal axis of the elastomer lining in the stator, while the angular contact support of rotation is located in the output part of the oscillator, and the transmission shaft is located between the output part of the rotor of the gerotor screw hydraulic motor and the input part of the hollow shaft of the angular contact support of rotation and is fastened with one edge to the output part of the rotor of the gerotor screw hydraulic motor , and with the other edge - with the input part of the shaft of the angular contact support of rotation, provides an increase in the resource and reliability of the oscillator for the drill string, a decrease in the friction forces of the drill string against the borehole walls, a decrease in torsional stresses in the drill string, an increase in the bit resource and an increase in the rate of penetration during drilling inclined and horizontal wells by increasing the energy characteristics of the pulsating pressure of the fluid and the mechanical power of the hydromechanical pulse generator with a given frequency and amplitude of the drill string vibrations with lower pressure losses.

When pumping a fluid (drilling mud) under a pressure of, for example, 25 ÷ 35 MPa, an axial load acts on the rotor helical teeth of a gerotor screw hydraulic motor, directed downstream of the fluid flow.

The oscillator contains a transmission shaft made in the form of a cardan shaft, including two couplings, each coupling covers the edge of the shaft, between each coupling and the edge of the shaft there is a number of drive mechanisms made in the form of a row of balls, with the possibility of transmitting the torque and angular displacement, and also placed thrust bearings for perceiving the longitudinal compressive load on the shaft, and inside each coupling there is a thrust ring secured by a threaded bushing, with the possibility of limiting the movement of the rotor of the gerotor screw hydraulic downhole motor, fastened to the shaft, against the flow of the fluid medium.

The oscillator contains an angular contact support of rotation, designed to hold the rotor of the gerotor screw hydraulic motor, fastened to the cardan shaft and the hollow shaft of the said angular contact support of rotation from longitudinal movements associated with the occurrence of an axial load directed downstream of the fluid flow, as well as from rotor weight (when drilling vertical wells).

Such an implementation of the oscillator for the drill string provides "unloading" of the rotor of the gerotor screw hydraulic motor, fastened to the cardan shaft and the hollow shaft of the angular contact support of rotation from the longitudinal movements associated with the occurrence of an axial load directed downstream of the fluid flow acting on the valve drive mechanism , in essence, forms a protective layer of fluid (drilling mud) between the ends of the valve sleeves, thereby eliminating shock loads on the ends of the valve sleeves made of hard alloy, increasing the fatigue strength of the valve sleeves in the valve elements, providing "soft" and silent operation of the valve pair.

At the same time, damping of hydrodynamic loads acting on the valve drive mechanism is provided due to the fact that the throttle sleeve of the stationary valve element fastened to the body is located adjacent downstream to the generator of hydromechanical impulses, the internal profile of the flow channel fastened to the body of the throttle sleeve of the stationary valve element is converging downward along flow (with a critical section), when the fluid flows through the confuser channel of a fixed throttle sleeve with a critical section, a pressure drop is created, at the outlet of the channel, the flow velocity increases, as a result of which the fluid pressure drops, a low pressure zone is formed at the outlet of the throttle sleeve, differential pressure across the throttle sleeve, which acts on the plunger module and the throttle sleeve attached to it and tends to move the plunger module and the throttle sleeve attached to it towards the end of the movable throttle sleeve.

As a result, the action of a fluid flow flowing from a throttle sleeve with a flow channel attached to the plunger module, the internal profile of which is diffuser downstream, inside the plunger module, which includes an elastomer lining fixed inside it and mounted on the tubular shank of the movable valve element with the possibility of rotation and longitudinal movement relative to the tubular shank of the valve element located at the inlet to the gerotor screw hydraulic motor and attached to the inlet part of the rotor of the gerotor screw hydraulic motor, in the partially overlapped position of the valve flow section, directed in the opposite direction - against the fluid flow (the rotor is motionlessly held in longitudinal direction by the cardan shaft and the hollow shaft of the angular contact support of rotation), and tends to move the plunger module and the throttle sleeve attached to it in the upstream direction, with the planetary With the rotation of the engine rotor, the plunger module and the throttle sleeve attached to it, these processes are cyclically repeated, and a damping layer of fluid is formed between the ends of the valve sleeves, which protects the ends of the valve sleeves from impacts and wear.

Implementation of the oscillator for the drill string in such a way that the angular contact support of rotation is located in the output part of the oscillator, and the transmission (cardan) shaft is located between the output part of the rotor of the gerotor screw hydraulic motor and the inlet part of the hollow shaft of the radial contact support of rotation and is fastened with one edge to the output part of the rotor of the gerotor screw hydraulic motor, and the other edge with the input part of the shaft of the angular contact support of rotation, increases the equivalent stresses (according to von Mises), which, taking into account the safety margin, the cardan shaft can perceive from the tightening torque of the cardan shaft thread, in which it becomes compressive load associated with holding the rotor in the longitudinal direction by the cardan shaft to damp the hydrodynamic loads acting on the valve drive mechanism and the shear force (eccentricity) of a rotor planetary rotating in an elastomer lining with helical teeth transmitting torque moment on the driveshaft.

Execution of the oscillator for the drill string in such a way that the maximum clearance between the end of the throttle sleeve, fastened to the plunger module of the movable valve element, and the end of the throttle sleeve, fastened to the body of the stationary valve element, is equal to the eccentricity of the central longitudinal axis of the tubular liner of the movable valve element relative to the central longitudinal the rotor axis of the gerotor screw hydraulic motor, increases the energy characteristics of the pulsating pressure of the fluid medium and the mechanical power of the generator of hydromechanical impulses with a given frequency and amplitude of oscillations of the drill string with lower pressure losses.

Below is an oscillator OS-172RS.800 for a drill string, designed to create hydromechanical impulses acting on a drill string in a well.

FIG. 1 shows an oscillator for creating hydromechanical impulses acting on a drill string in a well.

FIG. 2 shows element I in FIG. 1 of the plunger module and valve, the axis of the diffuser channel of the movable sleeve is offset relative to the central longitudinal axis of the engine rotor, the maximum clearance in the valve pair, the coaxial arrangement of the converging channel of the stationary sleeve and the elastomer lining in the stator.

FIG. 3 shows element I in FIG. 1 plunger module and valve, the axis of the diffuser channel of the movable sleeve is offset relative to the central longitudinal axis of the engine rotor, the minimum clearance in the valve pair, the minimum flow area of the valve.

FIG. 4 shows element I in FIG. 1 plunger module and valve, coaxial arrangement of the flow channel of the stationary and movable bushings, the maximum flow area of the valve.

FIG. 5 shows a section A-A in Fig. 3 across the plunger module inside the oscillator housing.

FIG. 6 shows a gerotor screw hydraulic motor driving an oscillator valve mechanism.

FIG. 7 shows a section b-b in Fig. 6 across the gerotor screw hydraulic motor.

FIG. 8 shows element II in FIG. 1, angular contact bearing of rotation.

FIG. 9 shows element III in FIG. 1, generator of hydromechanical impulses.

FIG. 10 shows a section b-b in fig. 9 across the spline connection between the body and the mandrel in the hydromechanical pulse generator.

FIG. 11 shows a section L-G in Fig. 9 across the split impact ring installed in the annular groove between the ends of the outer splines of the mandrel in the generator of hydromechanical impulses.

The oscillator for the drill string contains a gerotor screw hydraulic motor 1, including a tubular stator 2 with a lining 3 of an elastomer (elastic-elastic material) fixed in it, for example, rubber of the R1 (DE) brand, with internal helical teeth 4 and located inside the lining 3 from an elastomer in a tubular stator 2, a rotor 5 with external helical teeth 6, the rotation of the rotor 5 is carried out by pumping a fluid 7 - drilling mud, which has a density of up to 1500 kg / m ³ , contains up to 2% sand and up to 5% oil products, under pressure, for example, 25 ÷ 35 MPa, the number of teeth 6 of the rotor 5 is one less than the number of teeth 4 of the lining 3 of the elastomer in the stator 2, the stroke 8, T of the internal helical teeth 4 in the lining 3 of the elastomer in the stator 2 and the stroke 9, T1 of the outer of the helical teeth 6 of the rotor 2 are proportional to their number of teeth, and the central longitudinal axis 10 of the rotor 5 and the central longitudinal axis 11 of the lining 3 made of elastomer in the stator 2 are displaced between themselves by the amount of eccentricity 12, e, while the number of starts, essentially, the ratio of the number of teeth 6 of the rotor 5 to the number of teeth 4 of the lining 3 made of elastomer is 4/5, shown in FIG. 1, 6, 7.

The stroke 8, T of the helical line of the internal helical teeth 4 of the lining 3 of the elastomer in the stator 2 (or the pitch P _{z of} each helical tooth 4) and the stroke 9, T1 of the outer helical teeth 6 of the rotor 2 (or the pitch P _{z of} each helical tooth 6) is equal to the distance on the pine surface between two positions of the point forming the line of the helical tooth, corresponding to its full revolution around the axis of the gear wheel, for example, around the central longitudinal axis 11 of the elastomer plate 3 fixed in the stator 2, or around the central longitudinal axis 10 of the rotor 5, is shown, for example, in GOST 16530-83, page 17, and also shown in FIG. 6, 7.

The oscillator for the drill string contains a valve 13, which includes a movable valve element 14 and a stationary valve element 15, the movable valve element 14 is equipped with a first valve plate 16 installed therein, and the stationary valve element 15 is equipped with a second valve plate (sleeve) 17 installed therein, and The stationary valve element 15 with the second valve plate (sleeve) 17 installed in it forms a valve hole 18 and has a longitudinal axis 19, the movable valve element 14 is fastened to the rotor 5 by means of a thread 20 with a given tightening torque and is movable in the transverse direction 21 with the planetary rotation of the helical rotor 5 relative to the helical teeth 4 of the lining 3 made of elastomer in the stator 2 and the simultaneous rotation of the said rotor 5 around its own longitudinal axis 10 in the direction opposite to the direction of planetary rotation, as well as the movable valve element 14 fastened with a thread 20 to the rotor 5, refer flax stationary valve element 15, in operation, the valve elements 14 and 15 interact, together forming a variable flow area 22 for the fluid 7 through the valve 13, shown in FIG. 1, 2, 3, 5.

The oscillator contains a plunger module 23 located between the movable valve element 14 and the valve pair: 16 and 17, which during operation forms a variable flow area 22 for the fluid 7 through the valve 13, shown in FIG. 1, 2, 4, 5.

The movable valve element 14, rigidly attached to the rotor 5 by the thread 20, is provided with a tubular shank 24, the inner cavity 25 of the tubular shank 24 of the movable valve element 14 is configured to communicate with the fluid flow 7 by means of holes 26 and form a flow channel 27 through the internal cavity 25 tubular shank 24 is shown in FIG. 1, 2, 3, 4, 5.

The plunger module 23 contains a lining 28 made of elastomer, for example, rubber grade R1 (DE), fixed inside it, mounted on the tubular shank 24 of the first valve element 14 with the possibility of rotation relative to the outer belt 29 of the tubular shank 24 of the movable valve element 14 and longitudinal movement relative to the outer the belt 29 of the tubular shank 24 of the movable valve element 14 is shown in FIG. 1, 2, 3, 4, 5.

The first valve plate 16 is made in the form of rigidly fastened (press fit) with the plunger module 23 of the throttle sleeve 30 (made of tungsten carbide), with a flow channel 31 (valve hole 18), the internal profile of which is made as a diffuser downstream 7, shown in Fig. 1, 2, 3, 4, 5.

The maximum displacement 32 of the central longitudinal axis 19 of the flow channel 31 installed in the plunger module 23 of the throttle sleeve 30, the internal profile of which is diffuser downstream 7, relative to the central longitudinal axis 10 of the rotor 5 of the gerotor screw hydraulic motor 1 is equal to the eccentricity value 12, e, of the central longitudinal the axis 10 of the rotor 5 of the gerotor screw hydraulic motor 1 relative to the central longitudinal axis 11 of the elastomer plate 3 in the stator 2 is shown in FIG. 1, 2, 3, 4, 5.

An elastomer lining 28, fixed on the inner surface 33 of the plunger module 23, is made with six longitudinal grooves 34 on the inner surface 35 of the lining 28 with the possibility of cooling and lubricating the rubbing parts: the outer belt 29 of the tubular shank 24 of the movable valve element 14 and the inner surface 35 of the lining 28 from the elastomer, part of the fluid flow 7 at the outlet of the flow channel 31 of the plunger module 23 mounted on the tubular shank 24 of the first valve element 14 with the possibility of rotation and longitudinal movement (play) relative to the outer belt 29 of the tubular shank 24 of the movable valve element 14, shown in FIG ... 1, 2, 3, 4, 5.

The oscillator contains a transmission shaft made in the form of a driveshaft 36, including two couplings 37 and 38, each coupling, respectively, 37 and 38, covers the edge, respectively, 39 and 40 of the driveshaft 36, between each coupling, respectively, 37 and 38 and the edge 39 and 40 of the propeller shaft 36, a number of drive mechanisms, respectively 41, 42, are arranged, each made in the form of a row of eight balls, respectively, 43, 44, with the possibility of transmitting the torque and angular displacement, and also spherical thrust bearings are placed, respectively , 45, 46 for the perception of a longitudinal compressive load on the propeller shaft 36, and inside each clutch, respectively, 37, 38, there are thrust rings, respectively, 47, 48, each fixed by a threaded sleeve, respectively, 49, 50, with the possibility of limiting displacement of the rotor 5 of the gerotor screw hydraulic motor 1, fastened to the cardan shaft 36, against the flow of the fluid 7 (with pulsations of the pressure of the fluid 7), shown in fig. 1.

The oscillator contains a radial thrust bearing 51 of rotation, designed to hold the rotor 5 of the gerotor screw hydraulic motor 1, fastened to the cardan shaft 36, from longitudinal movement associated with the occurrence of an axial load directed downstream of the fluid 7, as well as from the weight of the rotor 5 gerotor screw hydraulic motor 1 (when drilling vertical wells), and the perception of the compressive load associated with holding the rotor 5 of the hydraulic motor 1 in the longitudinal direction by the cardan shaft 36, as well as for damping the hydrodynamic loads acting on the valve 13, and the shear force (eccentricity) a rotor 5 planetary rotating in a lining 3 made of elastomeric material with helical teeth 6 transmitting torque to the cardan shaft 36, made in the form of a thrust radial multi-row ball bearing 52, and two identical radial sliding bearings 53, each consisting of an outer sleeve 54 and internal VTU Lines 55, located in the housing 56 of the radial-contact bearing 51 of rotation, and, accordingly, on the hollow shaft 57, is shown in FIG. 18.

The outer and inner bushings, respectively 54 and 55 of two identical radial slide bearings 53 are made, each, in the form of a single structure with plates 58 made of hard alloy, mainly of tungsten carbide, forming sliding surfaces between the bushings 54 and 55, while the plates 58 are fastened in each of the bushings 54, as well as in each of the bushings 55 between each other by impregnating the hard alloy with the components of the binder-solder, and the molten powder of the binder-solder for attaching the plates 58 of the hard alloy contains components in the following ratio, wt. %: Ni 32 ÷ 47, Fe 2, Cr 7 ÷ 14, Si 2, WC the rest, while the hollow shaft 57 is fastened to the coupling 38 of the propeller shaft 36 by the adapter 59 using the thread 60, shown in Fig. 18.

The oscillator contains a generator 61 of hydromechanical impulses and includes a housing 62 made of outer tubular elements 63, 64, 65, a mandrel 66 placed inside the housing 62, made of inner tubular elements 67, 68, telescopically connected to each other and fastened by a thread 69, as well as elements for transmitting the drill string torque - internal splines 70 inside the outer tubular element 63 of the housing 62 and the corresponding external splines 71 on the inner tubular element 67 of the mandrel 66 between the housing 62 and the mandrel 66 in longitudinal movement relative to each other, shown in FIG. 1, 9, 10.

In the upper part of the inner tubular element 67 there is an internal thread 72 intended for connection to the bottom of the upper part of the drill string (not shown), the external tubular elements 63 and 64 are fastened with threads 73, the external tubular elements 64 and 65 are fastened with a thread 74, in the lower part of the outer of the tubular element 65, an internal thread 75 is made, while drilling fluid 7 is pumped through the mandrel 66, for example, a clay polymer containing abrasive particles, for example, up to 2% sand with dimensions of 0.15 ÷ 0.95 mm and up to 5% of oil products with a density 1.16 ÷ 1.26 g / cm ³ , at a hydrostatic pressure, for example, 25 ÷ 35 MPa, is shown in Fig. nineteen.

The generator 61 hydromechanical impulses contains a spring module 76 (disc springs) between the housing 62 (outer tubular elements 63, 64, 65) and the mandrel 66 (inner tubular elements 67, 68), and also contains a thrust sleeve 77 between the upper thrust end 78 of the housing 62 (outer tubular member 63) and a spring module 76 is shown in FIG. nineteen.

The generator 61 of hydromechanical impulses contains the upper abutting end 79 of the splines 71 of the mandrel 66 (the inner tubular element 67) and the lower abutting end 80 of the housing 62 (the outer tubular element 65), simultaneously engaging and loading the spring module 76 during the longitudinal compression of the housing 62 and the mandrel 66 relative to each other friend is shown in FIG. nineteen.

The generator 61 hydromechanical impulses contains the upper abutting end 78 of the housing 62 (outer tubular element 63) and the lower abutting end 81 of the mandrel 66 (inner tubular element 68), simultaneously engaging and loading the spring module 76 (disc springs) through the thrust sleeve 77 located between the upper the stop end 78 of the body 62 (outer tubular element 63) and the spring module 76 when the body 62 and the mandrel 66 are stretched relative to each other, is shown in FIG. nineteen.

The generator 61 hydromechanical impulses contains an annular (floating) piston 82 with seals 83 of elastomeric material on its outer surface 84 and seals 85 on its inner surface 86, installed between the inner surface 87 of the outer tubular element 65 of the housing 62 and the outer surface 88 of the inner tubular element 68 a mandrel 66 responsive to the pressure of the fluid 7 (drilling mud) pumped inside the mandrel 66 and the housing 62 under a pressure of, for example, 25 ÷ 35 MPa, is shown in FIG. nineteen.

The generator 61 hydromechanical impulses contains seals 89 in the upper part 90 between the body 62 and the mandrel 66 and a chamber 91 for working fluid-oil, for example, Mobilube I SHC 75W-90, limited by seals 89 in the upper part 90 of the body 62 and seals 83, 85 of the annular of the (floating) piston 82 between the housing 62 and the mandrel 66, and also includes a thrust ring 92 mounted by threads 93 on the inner tubular member 68 constituting the bottom 94 of the mandrel 66, shown in FIG. nineteen.

An annular (floating) piston 82 with seals 83 on its outer surface 84 and seals 85 on its inner surface 86, mounted between the inner surface 87 of the outer tubular element 65 of the housing 62 and the outer surface 88 of the inner tubular element 68 of the mandrel 66, separates the chamber 91 for the working liquid-oil, for example, Mobilube I SHC 75W-90, limited by seals 89 in the upper part 90 of the body 62 and seals 83, 85 of the annular piston 82 between the body 62 and the mandrel 66, from the inner cavity 95 of the mandrel 66 and the body 62 through which it is pumped drilling mud 7 at a hydrostatic pressure, for example, 25 ÷ 35 MPa, which helps to stretch the body 62 and the mandrel 66 relative to each other, is shown in Fig. nineteen.

In the generator 61 of hydromechanical impulses, the drive for transferring the torque between the mandrel 66 and the housing 62 (for rotating the drill string) during longitudinal movement relative to each other, essentially, elements for transmitting torque: the outer splines 71 of the part 67 of the mandrel 66 between the housing 62 and the mandrel 66 and the corresponding internal splines 70 of the upper part 63 of the housing 62, is provided with an impact ring 96 installed in the inner tubular element 67 of the mandrel 66 with the possibility of longitudinal movement of the mandrel 66 with the impact ring 96 inside the thrust sleeve 77, while the impact ring 96 is split in the meridian direction 97, consists of two parts 98, 99 and is installed in the annular groove 100 between the ends 101 and 102 of the outer splines 71 of the inner tubular element 67 of the mandrel 66 with the possibility of longitudinal movement of the mandrel 66 with the impact ring 96 (98, 99) inside the thrust sleeve 77, housed in the outer tubular member 64 of the housing 62 is shown in FIG. 9, 10, 11.

In the generator 61 of hydromechanical impulses when the housing 62 and the mandrel 66 are stretched relative to each other, the longitudinal travel is, for example, a value equal to the width of the annular groove 100 between the ends 101 and 102 of the outer splines 71 of the mandrel 66 (inner tubular element 67), and the longitudinal travel 103 when longitudinal compression of the body 62 and the mandrel 66 relative to each other is, for example, a value equal to the distance from the stop end 78 of the outer tubular element 63 to the end 104 of the outer splines 71 of the mandrel 66 (inner tubular element 67), shown in FIG. 9, 10, 11.

The longitudinal travel 103 with compression of the housing 62 and the mandrel 66 relative to each other is limited by the maximum travel of the impact ring 96, consisting of two parts 98, 99, inside the thrust sleeve 77, located in the outer tubular element 64 of the housing 62, until it stops against the end 78 of the outer tubular element 64, which makes it possible to apply an ultra-high load during operation with a hydro-mechanical jar (for an upward impact) to release it from a sticking in the BHA when drilling deviated and horizontal wells, is shown in FIG. 9, 10, 11.

The throttle sleeve 17 of the stationary valve element 15 attached to the body 105 is located adjacent downstream 7 to the generator 61 of hydromechanical impulses, the inner profile 106 of the flow channel 107 fastened to the body 105 of the throttle sleeve 17 of the stationary valve element 15 is converging downstream 7, shown in FIG. ... 1, 2, 3, 4, 5.

A plunger module 23, including a lining 28 made of an elastomer, for example, rubber grade R1 (DE), fixed inside it, mounted on a tubular shank 24 of a movable valve element 14 with the possibility of rotation and longitudinal movement relative to a tubular shank 24 of a valve element 14, is located at the inlet 108 into the gerotor screw hydraulic motor 1 and is attached to the inlet part 109 of the rotor 5 of the gerotor screw hydraulic motor 1 by the thread 20, shown in FIG. 1, 2, 3, 4, 5.

The movable valve element 14 is made in the form of a throttle sleeve 30 fastened (press fit) to the plunger module 23 with a flow channel 31, the internal profile of which is made of a diffuser downstream 7, and the central longitudinal axis 19 of the flow channel 31 installed in the said plunger module 23 of the throttle sleeve 30 is displaced relative to the central longitudinal axis 10 of the rotor 5 of the gerotor helical hydraulic motor 1, and the maximum displacement 32 of the central longitudinal axis 19 of the flow channel 31 installed in the plunger module 23 of the throttle sleeve 30, the internal profile of which is made diffuser downstream 7, relative to the central longitudinal axis 10 the rotor 5 of the gerotor screw hydraulic motor 1 is equal to the value of the eccentricity 12, e, the central longitudinal axis 10 of the rotor 5 of the gerotor screw hydraulic motor 1 relative to the central longitudinal axis 11 of the elastomer lining 3 in the stator 2, shown in FIG. 1, 2, 3, 4, 5.

Angular contact support 51 of rotation, designed to hold the rotor 5 of the gerotor screw hydraulic motor 1, fastened to the cardan shaft 36, from the longitudinal movement associated with the occurrence of an axial load directed downstream of the fluid 7, as well as from the weight of the rotor 5 of the gerotor screw hydraulic motor 1 (when drilling vertical wells), and the perception of the compressive load associated with holding the rotor 5 of the hydraulic motor 1 in the longitudinal direction by the cardan shaft 36, as well as for damping the hydrodynamic loads acting on the valve 13, and the shear force (eccentricity) of the planetary rotating in the lining 3 of the elastomeric material of the rotor 5 with helical teeth 6 transmitting torque to the propeller shaft 36, made in the form of a thrust radial multi-row ball bearing 52, and two identical radial sliding bearings 53, each consisting of an outer sleeve 54 and an inner bushings 55 placed in the housing 56 of the angular contact bearing 51 of rotation, and, accordingly, on the hollow shaft 57, is located in the output part - in the housing 56 of the oscillator, shown in FIG. 18.

The transmission shaft, made in the form of a propeller shaft 36, including two couplings 37 and 38, each coupling, respectively 37 and 38, covers the edge, respectively, 39 and 40 of the propeller shaft 36, between each coupling, respectively, 37 and 38 and the edge 39 and 40 of the propeller shaft 36, a number of drive mechanisms, respectively 41, 42, are placed, each made in the form of a row of eight balls, respectively, 43, 44, with the possibility of transmitting the moment of rotation and angular displacement, and also spherical thrust bearings are placed, respectively 45 , 46 for the perception of the longitudinal compressive load on the propeller shaft 36, and inside each clutch, respectively, 37, 38, there are thrust rings, respectively, 47, 48, each fixed by a threaded sleeve, respectively, 49, 50, with the possibility of limiting the movement of the rotor 5 of the gerotor screw hydraulic motor 1, fastened to the cardan shaft 36, against the flow of the fluid 7 (at pulsations of the pressure of the fluid 7), is placed between the outlet part 110 of the rotor 5 of the gerotor screw hydraulic motor 1 and the inlet part - the adapter 59, fastened to the hollow shaft 57 of the angular contact bearing of rotation 52, is shown in FIG. 1.6, 8.

The transmission shaft, made in the form of a cardan shaft 36, is fastened with one edge - the coupling 37 of the cardan shaft 36 with the output part 110 of the rotor 5 of the gerotor screw hydraulic motor 1 using the thread 111, and the other edge: the coupling 38 of the cardan shaft 36 and the adapter 59 - with the input part 112 of the hollow shaft 57 of an angular contact bearing of rotation 52 by means of a thread 60 is shown in FIG. 1.6, 8.

The maximum clearance 113 between the end face 114 of the throttle sleeve 30, fastened to the plunger module 23 of the movable valve element 14, and the end face 115 of the throttle sleeve 17, fastened to the body 105 together with the stationary valve element 15, is equal to the eccentricity 12 e of the central longitudinal axis 19 of the tubular shank 24 of the movable valve element 14 relative to the central longitudinal axis 10 of the rotor 5 of the gerotor screw hydraulic motor 1 is shown in FIG. 1.2, 3.

In this case, the outer chord 29 of the tubular shank 24 of the movable valve element 14, the flow channel 18, 31 of the throttle sleeve 16, 30, the inner profile of which is made diffuser downstream 7, and the flow channel 27 for the fluid 7 through the inner cavity 25 of the tubular shank 24 on the inlet 108 of the gerotor screw hydraulic motor 1 is located coaxially with each other, shown in FIG. 2, 3, 5, 6.

In addition, item 116 is the external thread of the body 56 of the angular contact bearing 51 of rotation, intended for connection with the top of the lower part of the drill string (not shown), is shown in FIG. 1.

In the wells of the regions of the Russian Federation in the BHA, gerotor screw hydraulic motors and hydraulic jars are used (patents RU 2515627, RU 2439284, LLC "Firm" Radius-Service), as well as the claimed oscillator for a drill string for driving directional wells with a horizontal end.

The oscillator for the drill string is placed in the drill string above the drill jar and drill collar, the BHA contains a D-172RS gerotor hydraulic motor with a skew angle regulator and a bit, as well as downhole telemetry system modules - measurement (MWD) and logging (LWD) modules.

The horizontal wellbore is drilled with the rotation of the drill string by the rotor of the 5000EU drilling rig with a rotational speed of 20-30 rpm, with the joint operation of the gerotor screw hydraulic motor rotating the bit, while the flow of drilling fluid 7 provides flushing of the bottom of the well and removal of the drilled rock to the surface.

The oscillator for the drill string works as follows: the flow of drilling mud 7 containing solid abrasive particles, for example, up to 2% sand with dimensions of 0.15 ÷ 0.95 mm and up to 5% oil products polymer - clay drilling mud with a density of 1.16 ÷ 1 , 26 g / cm ³ , pumped by a pump of a drilling rig at a hydrostatic pressure, for example, 25 ÷ 35 MPa, through the drill pipe.

The drilling mud 7 is pumped through the inner cavity 95 of the mandrel 66, fastened by the thread 72 to the bottom of the upper part of the drill string, in the generator 61 of hydromechanical impulses, while the annular (floating) piston 82 with seals 83 on its outer surface 84 and seals 85 on its inner surface 86, mounted between the inner surface 87 of the outer tubular element 65 of the housing 62 and the outer surface 88 of the inner tubular element 68 of the mandrel 66, acts on the chamber 91 for working fluid-oil, limited by the seals 89 in the upper part 90 of the housing 62 and the seals 83, 85 of the annular piston 82 between the casing 62 and the mandrel 66 from the inner cavity 95 of the mandrel 66 and the casing 62, through which the drilling fluid 7 is pumped at hydrostatic pressure, which helps to stretch the casing 62 and the mandrel 66 relative to each other and the constant readiness of the generator 61 of hydromechanical impulses to work in the well, shown in FIG. nineteen.

The drilling mud 7 is pumped through the throttle sleeve 17 of the fixed valve element 15 attached to the part 105 of the housing 62, which is located adjacent downstream 7 to the generator 61 of hydromechanical impulses, and the inner profile 106 of the flow channel 107 is attached to the part 105 of the housing 62 of the throttle sleeve 17 of the fixed valve element 15 is made converging downstream 7, then the drilling fluid 7 is pumped through a movable valve element 14 made in the form of a throttle sleeve 30 fastened to the plunger module 23 with a flow channel 31, the internal profile of which is made of a diffuser downstream 7, then the drilling mud 7 is pumped through multi-threaded screw (sluice) chambers between the outer helical teeth 6 of the helical rotor 5 of the hydraulic motor 1 and the inner helical teeth 4 of the elastomer lining 3 fixed in the stator 2, while the flow of the drilling fluid 7 forms a high pressure area and the torque from the hydraulic systems l, which drives the rotor 5 of the hydraulic motor 1 inside the elastomeric plate 3 fixed in the stator 2 into planetary-rotor rotation, is shown in FIG. 1, 2, 3, 4, 5, 6, 7.

Screw multi-port (isolated) chambers between the helical teeth of the rotor 5 and the helical teeth of the elastomeric lining 3 fixed in the stator 2, under the action of the pumping supply of the drilling fluid 7, periodically move along the flow of the drilling fluid 7.

When pumping a fluid 7 (drilling mud) under a pressure of, for example, 25 ÷ 35 MPa, an axial load directed downstream of the fluid 7 acts on the helical teeth 6 of the rotor 5 of the gerotor screw hydraulic motor 1.

The planetary-rotor rotation of the helical rotor 5 inside the elastomer lining 3, fixed in the stator 2, transmits the torque (in the opposite direction) to the plunger module 23, located between the movable valve element 14 and the valve pair: 16 and 17, which during operation forms a variable bore section 22 for the fluid 7 through the valve 13, as well as onto the transmission shaft, made in the form of a driveshaft 36, fastened by one edge - the coupling 37 of the driveshaft 36 with the output part 110 of the rotor 5 of the gerotor screw hydraulic motor 1 using the thread 111, and the other edge: coupling 38 of the propeller shaft 36 and adapter 59 - with the entrance part 112 of the hollow shaft 57 of the angular contact support of rotation 52 using the thread 60, as well as on the radial support 51 of rotation, designed to hold the rotor 5 of the gerotor screw hydraulic motor 1, fastened to the propeller shaft 36, from the longitudinal movement associated with the occurrence of an axial load, directed downstream of the fluid 7, as well as from the weight of the rotor 5 of the gerotor screw hydraulic motor 1 (when drilling vertical wells), and the perception of the compressive load associated with holding the rotor 5 of the hydraulic motor 1 in the longitudinal direction by the cardan shaft 36, as well as for damping hydrodynamic loads acting on the valve 13, and the shear force (eccentricity) of the rotor 5 planetary rotating in the lining 3 made of elastomeric material with helical teeth 6 transmitting torque to the propeller shaft 36, made in the form of a thrust radial multi-row ball bearing 52, and two identical radial sliding bearings 53, each consisting of an outer sleeve 54 and an inner sleeve 55, located in the housing 56 of the angular contact bearing 51 of rotation, and, accordingly, on the hollow shaft 57, located in the output part - in the housing 56 of the oscillator.

The movable valve element 14, rigidly fastened to the rotor 5 by the thread 20, is provided with a tubular shank 24, while the inner cavity 25 of the tubular shank 24 of the movable valve element 14 communicates through the holes 26 with the fluid flow 7 and forms a flow channel 27 through the inner cavity 25 of the tubular shank 24, and the plunger module 23 containing an elastomer lining 28 fixed inside it and mounted on the tubular shank 24 of the first valve element 14 rotates relative to the outer collar 29 of the tubular shank 24 of the movable valve element 14 with the possibility of longitudinal movement (backlash) relative to the outer collar 29 the tubular shank 24 of the movable valve member 14 is shown in FIG. 1, 2, 3, 4, 5.

An elastomer lining 28, fixed on the inner surface 33 of the plunger module 23, made with longitudinal grooves 34 on the inner surface 35 of the lining 28, provides damping of the plunger module 23, as well as lubrication and cooling with drilling mud 7 of the outer belt 29 of the tubular shank 24 of the movable valve element 14 during rotation and longitudinal movement of the plunger module 23 is shown in FIG. 1, 2, 3, 4, 5.

Changing the variable flow area 22 for the drilling fluid 7 through the plunger module 23 and the valve 13 creates a pressure pulsation in the drilling fluid 7, the action of which is transmitted to the annular piston 82 with seals 83 on the outer surface 84 and seals 85 on the inner surface 86, installed between the inner surface 88 of the outer tubular element 65 of the housing 62 and the outer surface 88 of the inner tubular element 68 of the mandrel 66, responsive to the pressure of the drilling fluid 7 pumped inside the mandrel 66 and the housing 62 under a pressure of 25 ÷ 35 MPa, in the generator 62 of hydromechanical impulses made of outer tubular elements 63, 64, 65, a mandrel 66 placed inside the housing 62, made of inner tubular elements 67, 68, telescopically connected to each other and fastened by a thread 69, as well as elements for transmitting the drill string torque - internal splines 70 inside the outer tubular element 63 of the housing 62 and external spline 71 on the inner tubular member 67 of the mandrel 66 between the body 62 and the mandrel 66 in longitudinal displacement relative to each other is shown in FIG. 1, 9, 10.

In this case, the generator 61 hydromechanical impulses, responsive to the pressure of the fluid 7 (drilling mud), pumped inside the mandrel 66 and the housing 62 under a pressure of 25 ÷ 35 MPa, excites longitudinal cyclic oscillations of the drill string with a frequency of 12 ÷ 19 Hz at a drilling mud flow rate of 30 liters /from.

Execution of the oscillator for the drill string in such a way that the throttle sleeve 17 of the stationary valve element 15 attached to the body 105 is located adjacent downstream 7 to the generator 61 of hydromechanical impulses, the inner profile 106 of the flow channel 107 attached to the body 105 of the throttle sleeve 17 of the stationary valve element 15 is made converging downstream 7, the plunger module 23, including an elastomer lining 28 fixed inside it, mounted on the tubular shank 24 of the movable valve element 14 with the possibility of rotation and longitudinal movement relative to the tubular shank 24 of the valve element 14, is located at the inlet 108 to the gerotor helical hydraulic engine 1 and is attached to the inlet part 109 of the rotor 5 of the gerotor helical hydraulic motor 1 by the thread 20, while the movable valve element 14 is made in the form of a throttle sleeve 30 attached to the plunger module 23 with a flow channel 31, the inner hole the filter of which is made diffuser downstream 7, and the central longitudinal axis 19 of the flow channel 31 installed in the said plunger module 23 of the throttle sleeve 30 is displaced relative to the central longitudinal axis 10 of the rotor 5 of the gerotor screw hydraulic motor 1, and the maximum displacement 32 of the central longitudinal axis 19 of the flow channel 31 installed in the plunger module 23 of the throttle sleeve 30, the internal profile of which is made diffuser downstream 7, relative to the central longitudinal axis 10 of the rotor 5 of the gerotor screw hydraulic motor 1 is equal to the eccentricity value 12, e, the central longitudinal axis 10 of the rotor 5 of the gerotor screw hydraulic motor 1 relative to the central longitudinal axis 11 of the lining 3 made of elastomer in the stator 2, while the radial thrust bearing 51 of rotation, designed to hold the rotor 5 of the gerotor screw hydraulic motor 1, fastened to the cardan shaft 36, from longitudinal movement, associated with the occurrence of an axial load directed downstream of the fluid 7, as well as from the weight of the rotor 5 of the gerotor screw hydraulic motor 1 and the perception of the compressive load associated with holding the rotor 5 of the hydraulic motor 1 in the longitudinal direction by the cardan shaft 36, as well as for damping the hydrodynamic loads acting on the valve 13, and the skewing forces of the rotor 5, planetary rotating in the lining 3 made of elastomer, with helical teeth 6 transmitting torque to the propeller shaft 36, made in the form of a thrust radial multi-row ball bearing 52, located in the output part - in the housing 56 of the oscillator, while the transmission shaft, made in the form of a driveshaft 36, is fastened with one edge - the coupling 37 of the driveshaft 36 with the output part 110 of the rotor 5 of the gerotor screw hydraulic motor 1 using the thread 111, and the other edge: the coupling 38 of the driveshaft 36 and adapter 59 - with the entrance part 112 of the hollow shaft 57 r The radial-thrust bearing of rotation 52 using the thread 60 provides an increase in the resource and reliability of the oscillator for the drill string, a decrease in the friction forces of the drill string against the borehole walls, a decrease in torsional stresses in the drill string, an increase in the bit life and an increase in the rate of penetration when drilling inclined and horizontal wells by increasing the energy characteristics of the pulsating pressure of the fluid and the mechanical power of the hydromechanical impulse generator and the operating range of the frequency and amplitude of the drill string oscillations with lower pressure losses.

The design of the oscillator for the drill string in such a way that the plunger module 23 contains an elastomer lining fixed inside it is mounted on the tubular shank 24 of the first valve element 14 with the possibility of rotation relative to the outer belt 29 of the tubular shank 24 of the movable valve element 14 and longitudinal movement relative to the outer belt 29 tubular shank 24 of the movable valve element 14, while the lining 28 made of elastomer, fixed on the inner surface 33 of the plunger module 23, is made with six longitudinal grooves 34 on the inner surface 35 of the lining 28 with the possibility of cooling and lubricating the rubbing parts: the outer belt 29 of the tubular shank 24 of the movable valve element 14 and the inner surface 35 of the lining 28 made of an elastic-elastic material part of the fluid flow 7 at the exit from the flow channel 31 of the plunger module 23 mounted on the tubular shank 24 of the first valve element 14 with the possibility rotation and longitudinal movement (backlash) relative to the outer belt 29 of the tubular shank 24 of the movable valve element 14, provides hydraulic compensation of the valve sleeves 31, 17 by the flow of fluid 7, essentially forms a protective layer of fluid 7 (drilling mud) between the ends 44 and 45 of the valve bushings 30 and 17, as a result of this, the shock loads on the ends 114 and 115 of the valve bushings 30 and 17 of hard alloy are reduced, the fatigue endurance and strength of the valve bushings 30 and 17 made of hard alloy in the valve elements 14, 15 are reduced, and "soft" and quiet valve operation 13.

The implementation of the oscillator for the drill string in such a way that the generator 61 of hydromechanical impulses contains a drive for transferring the torque between the mandrel 66 and the housing 62 (for rotating the drill string) during longitudinal movement relative to each other, essentially elements for transmitting torque: external splines 71 of the part 67 of the mandrel 66 between the body 62 and the mandrel 66 and the corresponding internal splines 70 of the upper part 63 of the casing 62, provided with an impact ring 96 installed in the inner tubular element 67 of the mandrel 66 with the possibility of longitudinal movement of the mandrel 66 with the impact ring 96 inside the thrust sleeve 77 , wherein the impact ring 96 is split in the meridian direction 97, consists of two parts 98, 99 and is installed in the annular groove 100 between the ends 101 and 102 of the outer splines 71 of the inner tubular element 67 of the mandrel 66 with the possibility of longitudinal movement of the mandrel 66 with the impact ring 96 (98, 99) inside the thrust sleeve 77, times Placed in the outer tubular element 64 of the housing 62, it is possible to apply an ultra-high axial load (190,000 kgf) to the oscillator when operating with a hydromechanical jar (for an upward shock) in the drill string assembly to release it from a sticking.

The invention provides an increase in the resource and reliability of an oscillator for a drill string, a decrease in the friction forces of the drill string against the borehole wall, a decrease in torsional stresses in the drill string, an increase in the bit life and an increase in the rate of penetration when drilling inclined and horizontal wells by increasing the energy characteristics of the pulsating fluid pressure and mechanical power of the generator of hydromechanical impulses with a given frequency and amplitude of oscillations of the drill string with lower pressure losses.

Claims (2)

1. An oscillator for a drill string, containing a gerotor screw hydraulic motor, including a tubular stator with an elastomer lining fixed in it with internal helical teeth and a rotor with external helical teeth located inside the stator, the rotation of the rotor is carried out by pumping a fluid medium, the number of rotor teeth per unit less number of teeth of the elastomer lining, the strokes of the helical teeth of the elastomer lining and rotor are proportional to their numbers of teeth, and the central longitudinal axes of the rotor and the elastomer lining in the stator are displaced between themselves by the amount of eccentricity, and the valve including the movable valve element and the stationary valve element, the movable valve element is provided with a first valve plate installed in it, the stationary valve element is equipped with a second valve plate installed therein, and the stationary valve element with the second valve plate installed therein forms a valve opening and has a longitudinal axis b, the movable valve element has the ability to move relative to the stationary valve element, and during operation, the valve elements interact, jointly forming a variable flow area for the fluid through the valve, and also containing a plunger module, in which the movable valve element is equipped with a tubular shank, the inner cavity of the tubular shank of the movable valve element is configured to communicate with the fluid flow and form a flow channel through the inner cavity of the tubular shank, and the plunger module contains an elastomer lining fixed inside it and is mounted on the tubular shank of the movable valve element with the possibility of rotation and longitudinal movement relative to the tubular shank of the movable valve element, while the first valve plate is made in the form of a first throttle sleeve with a flow channel fastened to the plunger module, and the second valve plate is made in the form of attached to the body of the second throttle sleeve with a flow channel, and also containing a transmission shaft, an angular contact support of rotation, including a hollow shaft installed in an angular contact support of rotation with the possibility of rotation, and a generator of hydromechanical impulses containing a body made of external tubular elements , placed inside the body, a mandrel made of inner tubular elements telescopically interconnected, elements for transferring the torque between the body and the mandrel during longitudinal movement relative to each other, these tubular elements are equipped with threads, and also containing a spring module between the body and the mandrel, thrust a bushing between the upper stop end of the housing and the spring module, said outer tubular elements having upper and lower stop ends located along the opposite edges of the spring module, the upper stop end of the first tubular element and the lower end of the second tubular element that, simultaneously engaging and loading the spring module during longitudinal compression of the said tubular elements relative to each other, the upper abutting end of the second tubular element and the lower abutting end of the first tubular element, simultaneously engaging and loading the spring module when stretching the said tubular elements relative to each other, the annular piston with seals on the outer and inner surfaces, installed between the inner surface of the body and the outer surface of the mandrel, responding to fluid pressure, and also containing seals in the upper part between the body and the mandrel and a chamber for working fluid - oil, limited by seals in the upper part of the body and seals of the annular piston between the body and the mandrel, and a thrust ring mounted on the inner tubular element constituting the lower part of the mandrel, while the drive for transmitting the torque between the mandrel and the body during longitudinal movement relative to each other the other is equipped with an impact ring installed in the mandrel with the possibility of longitudinal movement of the mandrel with an impact ring inside the thrust sleeve, characterized in that the throttle sleeve of the stationary valve element fastened to the body is located adjacent downstream to the generator of hydromechanical impulses, the internal profile of the flow channel attached to the throttle body the sleeve of the stationary valve element is converging downstream, the plunger module, including an elastomer lining fixed inside it and mounted on the tubular shank of the movable valve element with the possibility of rotation and longitudinal movement relative to the tubular shank of the valve element, is located at the inlet to the gerotor screw hydraulic motor and is fastened with the inlet part of the rotor of the gerotor screw hydraulic motor, while the movable valve element is made in the form of a throttle sleeve fastened to the plunger module with a flow channel, vn the morning profile of which is made diffuser downstream, and the central longitudinal axis of the flow channel installed in the said plunger module of the throttle sleeve is displaced relative to the central longitudinal axis of the rotor of the gerotor screw hydraulic engine, and the maximum displacement of the central longitudinal axis of the flow channel installed in the plunger module of the throttle sleeve, internal profile which is made diffuser downstream, relative to the central longitudinal axis of the rotor of the gerotor screw hydraulic motor, is equal to the value of the eccentricity of the central longitudinal axis of the rotor of the gerotor screw hydraulic motor relative to the central longitudinal axis of the elastomer lining in the stator, while the radial thrust bearing of rotation is located in the output part of the oscillator , and the transmission shaft is located between the output part of the rotor of the gerotor screw hydraulic motor and the input part of the hollow shaft of the angular contact support shcheniya and is fastened with one edge to the output part of the rotor of the gerotor screw hydraulic motor, and the other edge - to the input part of the shaft of the angular contact support of rotation. 2. An oscillator for a drill string according to claim 1, characterized in that the maximum clearance between the end of the throttle sleeve attached to the plunger module of the movable valve element and the end of the throttle sleeve attached to the body of the stationary valve element is equal to the eccentricity of the central longitudinal axis of the tubular shank of the movable valve element relative to the central longitudinal axis of the rotor of the gerotor screw hydraulic motor.

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