RU2689014C1 - Stator of screw gerotor hydraulic machine - Google Patents

Abstract

FIELD: soil or rock drilling.SUBSTANCE: invention relates to hydraulic drives for rotary drilling located in a well. Stator comprises a tubular housing with an inner surface made in the form of a helicoid with internal helical teeth, on each edge of the housing there is an internal thread, and also comprises an elastomer cover in housing adjacent to housing inner surface, elastomer cover is made with inner helical teeth and matches shape with internal helical teeth in the housing, and the thickness of the coating is maximum on teeth radially directed inwards. In the tubular housing, the maximum thickness of the elastomer cover along the valleys of its inner helical surface located at the maximum radial distance is half the height of its internal helical teeth, and the minimum wall thickness of the housing along the radially outwardly directed recesses of its inner helical surface is equal to the height of the inner helical teeth in the elastomer cover. In stator in downstream part of housing there is a damper cavity located downstream of internal screw teeth edge in housing directed against flow, made in form of annular groove inside housing, which adjoins to side surfaces of internal helical teeth of housing, formed by said annular groove, and the elastomer cover contains in the damper cavity an inlet damper from an elastomer with its own internal helical teeth adjoining the inner helical teeth of the elastomer cover adjacent to the surface of the annular groove inside the housing and the side surfaces of the inner helical teeth of the housing, formed by said annular groove, with possibility bonding to an elastomer coating, as well as with annular groove inside housing and side surfaces of internal helical teeth of housing, formed by said annular groove, wherein the minimum distance from the anti-flow edge of the inner helical teeth in the inlet downstream of the housing portion to the input edge of the input damper is equal to the thickness of the input damper from the elastomer on its inner helical teeth radially directed inward. Stator comprises in the downstream part of the tubular housing a damping cavity located upstream of the edge of internal helical teeth in the housing, directed downstream, made in the form of an annular groove inside the housing, adjacent to the side surfaces of the internal helical teeth of the housing, formed by said annular groove, and elastomer cover comprises in said damper cavity output damper from elastomer with its own internal helical teeth, adjacent to inner helical teeth of elastomer cover, adjacent to surface of annular groove inside housing and side surfaces of internal helical teeth of housing, formed by said annular groove, with possibility bonding to an elastomer cover, as well as with annular groove inside housing and side surfaces of internal helical teeth of housing, formed by said annular groove, wherein the minimum distance from the upstream edge of the inner helical teeth in the downstream portion of the housing to the output edge of the output damper is equal to the thickness of the output damper from the elastomer on its inner helical teeth radially directed inward.EFFECT: increased resource and reliability, accuracy of driving of inclined and horizontal wells, rate of set of parameters of well curvature, as well as improved cross-country capacity, that is reduced resistance and stress in assembly of bottom of drill string.1 cl, 10 dwg

Description

The invention relates to hydraulic actuators for rotary drilling, placed in the well, in particular to screw gyratory hydraulic motors for drilling oil wells.

Known helical hydraulic mechanism used as a pump or engine, comprising a stator housing and a rotor, wherein the rotor has an outer screw surface, the stator housing is designed as a monolithic rigid tubular element having a cylindrical outer surface and an inner surface, as well as having helical teeth, however, the above mechanism contains a flexible layer made of elastomer, having a uniform thickness on the inner surface of the housing (US 2005/0079083 A1, April 14, 2005).

In the well-known screw hydraulic mechanism, a flexible layer made of elastomer having a uniform thickness on the inner surface of the housing undergoes deformation and bending when the rotor rotates inside the stator in planetary-rotary rotation, which leads to the formation of zones on the projections and depressions of the teeth pressure, shear strength, hardness (elasticity) and thermal conductivity.

The temperature in the elastomer plate can increase, for example, to 60 ° C, and the increase in tension in the working pair can be, for example, up to 0.05 mm per diameter for every 10 ° C temperature increase.

A disadvantage of the known construction is the incomplete use of the possibility of increasing the service life and reliability of the screw hydraulic mechanism when using it in a downhole motor, as well as increasing the maximum power, torque on the output shaft in the maximum power mode and fatigue endurance (resource) of the elastomer facing - not less than 100 thousand cycles.

The disadvantages of the known construction are explained by the incomplete ability to optimize the thickness of the elastomer plate along the protrusions and cavities of the helical teeth, which leads to deterioration of internal heat removal from the elastomer plate to the flow of drilling fluid inside the housing, as well as through the housing walls to the flow of drilling mud in the annulus, the formation in the centers of the profile of the elastomeric plate of the zones of destruction of the material from the effects of a temperature gradient and an increase in tension in the working pair.

As a result, the profile center becomes less flexible (brittle and brittle), the mechanical properties of the elastomer, for example, rubber, significantly deteriorate in these areas, and the pressure acting in the chambers between the rotor and the stator may exceed the shear strength of the elastomer, and the tops of the teeth in facing deformed and detached from the body.

Known stator screw gyratory hydraulic pump or motor, comprising a housing with an inner surface, made with internal helical teeth, secured in the housing covered and covering the plates of the elastomer, while the circumferential facing is made with internal screw teeth, designed to accommodate the rotor having an outer surface helical teeth, the covering plate is bonded to the covered plate and to the inner surface of the housing, and the number of rotor teeth per unit it bigger number of housing teeth (US 6,881,045 A, 23.12.2004).

Known helical hydraulic mechanism contains a flexible layer made of elastomer, having the same thickness on the inner surface of the body, which leads to the formation on the protrusions and the depressions of the teeth zones that differ from each other in values of contact pressure, shear strength, hardness (elasticity) and thermal conductivity, which subjected to deformation and bending during the planetary-rotary rotor rotation inside the stator.

The disadvantages of the known construction are explained by the incomplete ability to optimize the thickness of the elastomer plate along the protrusions and cavities of the helical teeth, which leads to deterioration of internal heat removal from the elastomer plate to the flow of drilling fluid inside the housing, as well as through the housing walls to the flow of drilling mud in the annulus, the formation in the centers of the profile of the elastomeric plate of the zones of destruction of the material from the effects of a temperature gradient and an increase in tension in the working pair.

As a result, the profile center becomes less flexible (brittle and brittle), the mechanical properties of rubber or elastomer in these areas deteriorate significantly, and the pressure acting in the chambers between the rotor and the stator may exceed the shear strength of the elastomer, and the tops of the teeth in the plate are deformed and detached from the body.

A disadvantage of the known construction is also a high probability of destruction of the threaded joints of the tubular body when using a downhole motor in horizontal controlled layouts of the bottom of the drill string, in areas of curvature variation of an inclined well, as well as losing its stability mainly under axial load on the bit and shock impacts from the hydraulic jar in the composition bent drill pipe string, for example, when passing through radius sections of a wellbore during horizontal drilling and, which is explained by the fact that the stator is made of a composite: from a case, a smooth pipe covered by and covering the plates of elastomer, made in the form of a helicoid.

Covered lining of the same thickness is made of a material, for example, Ultra-Flex 114, and the additional covering plate with an inner surface in the form of a helicoid, essentially with internal helical multiple teeth, is made of a harder and more durable material.

At the same time, the known stator, when used in a screw gyratory hydraulic motor, does not provide significant advantages, for example, the maximum rate of curvature set (when drilling an inclined directional well) due to the destruction of the body, for example, when passing through the radius of the wellbore during horizontal drilling using a column drill pipe hydraulic jar, with the rotation of the curved string of drill pipe (20 ÷ 40 rpm), with shock loads and shock pulses from the jar, and also The effect of relaxation of tensile stresses in the curved string of drill pipe in which the engine is mounted.

The disadvantages of the known stator are also explained by cyclic loading of helical teeth made, for example, from elastomers of different shear strength, hardness and thermal conductivity, which are subjected to deformation and bending when the rotor rotates inside the rotor inside the stator, which leads to heat generation inside the tooth material, violation of tension the working pair, the detachment of the lining of the elastomer from the body, as well as the delamination between the lining of the elastomer due to the deterioration of the internal heat removal from the elastomer lining and through the layer of material through the walls of the housing to the drilling mud of the annulus.

The temperature in the elastomer plate may increase, for example, to 85 ° C, and the increase in tension in the working pair may be, for example, up to 0.08 mm per diameter for every 10 ° C temperature increase, which leads to off-design operating modes, not provides maximum power, torque on the output shaft in the mode of maximum power and permissible axial load with an increase in the maximum pressure drop (inter-turn, on the stator teeth) in the maximum power mode.

Known stator for hydraulic downhole motor, forming an outer pipe with an inner surface made of at least two internal helical teeth (or blades), fixed in the housing plate, for example, of elastomer, adjacent to the inner surface of the outer pipe, while the lining made with internal helical teeth (or blades), coincides in shape with internal helical teeth (or blades) in the outer tube, and the thickness of the lining is maximum on the teeth (or blades), radial inwardly directed (at least two) (US 6604921 B1, 14.04.2005).

A disadvantage of the known construction is the incomplete use of the possibility of increasing the reliability and service life of a downhole motor, maximum power, torque on the output shaft in the maximum power mode and fatigue endurance (resource) of the elastomer lining - not less than 100 thousand cycles.

Since the elastomer is characterized by high insulating properties, it delays the transfer of heat to a greater extent along the protrusions of the helical teeth compared to the hollows of these helical teeth.

The temperature in the lining of the elastomer may increase, for example, to 85 ° C, and the increase in tension in the working pair may be, for example, up to 0.08 mm per diameter for every 10 ° C temperature increase, which leads to off-design operating modes maximum power, moment of force on the output shaft in the mode of maximum power and permissible axial load with an increase in the maximum differential pressure (inter-turn, on the stator teeth) in the mode of maximum power.

The disadvantages of the known stator for a hydraulic downhole motor are explained by the incomplete use of the possibility of optimizing the lining thickness along the hollows of the inner screw surface and the minimum wall thickness of the outer tube relative to the height of the teeth in the lining, as well as the formation of zones on each protrusions and the troughs , shear strength, hardness (elasticity) and thermal conductivity, which are subjected to deformation and bending during the rotor planetary-rotary rotation and inside the stator, which leads to an increased temperature gradient when heat is generated inside the material of the teeth and a violation of tension in the working pair, deterioration of internal heat removal from the elastomer plate to the flow of drilling fluid inside the housing, as well as through the walls of the outer pipe to the drilling fluid in the annulus whose flow is directed from the bottom to the wellhead.

Due to the heat generated in the centers of the teeth, secondary polymerization occurs: molecular crosslinking of the elastomer (rubber), which leads to the destruction of the material, as a result, the center of the lining profile becomes inflexible (brittle and brittle), the mechanical properties of the elastomer in these areas deteriorate significantly, with Thereby, the pressure acting in the chambers between the rotor and the stator may exceed the shear strength of the elastomer, and the tops of the stator deform and detach from the stator.

The stator of a screw gyratory hydraulic machine is known, for example, a motor for rotating a rotor from pumping a fluid supply or a pump for feeding a fluid due to a rotating rotor, comprising an outer tube with an inner surface made in the form of a helicoid with inner helical teeth; the elastomer adjacent to the inner surface of the outer pipe, while the lining is made with internal helical teeth and coincides in shape with the internal screw teeth in the outer pipe, and t The lining thickness is maximum on the teeth, radially inward, in the outer pipe, the maximum thickness of the lining of the elastomer along the hollows of its inner screw surface, located at the maximum radial distance, is equal to half the height of its internal helical teeth, and the minimum wall thickness of the outer pipe along radially outwards the hollows of its inner screw surface is equal to the height of the internal helical teeth in the lining of elastomer (RU 2373364 C2, November 20, 2009).

The main defects that reduce the reliability and life of the downhole motor, in which the known stator is made with the same thickness of an elastomer plate (R-Wall): cracking of the plate of elastomer (rubber) at the edges, from the inlet and outlet of the fluid (drilling mud), delamination plates of elastomer (rubber) along the edges, from the inlet and outlet of the fluid, as well as tearing pieces of the plate of elastomer (rubber) along the edges - in the inlet and downstream parts of the plate of elastomer in the stator in tense working conditions (during drilling in solid rocks): if the required tension is in the working pair between the rotor and the lining of the tubular body, the contact pressure is 2.5 ÷ 3 MPa, the sliding speed is 0.5 ÷ 2.5 m / s, the hydrostatic pressure can reach 50 MPa, and the moment of force on the output shaft in maximum power mode can reach 30 kN m, and under conditions of high turbulence of the drilling fluid, which has a density of up to 1500 kg / m ³ , contains up to 2% sand and up to 5% of oil products, which leads to cessation of circulation, the main reason for the failure The mounting of the bottom of the drill string (BHA), in which the motor section with the spindle and the bit is installed, is “rubber in the bit”.

The development of these defects is promoted by high working pressure drops, internal heat generation in the material of the stator lining, braking of the working pair during operation, high tension in the working pair.

Increasing the length of the section of working pairs can significantly reduce the level of contact loads in the engagement of the working pair and prevent premature destruction of the elastomer plate at the edges of the stator.

At the same time, the energy performance of the engine, reliability and resource increase. However, an increase in the length of the rotor-stator working steam impairs the permeability of the bottom-hole assembly as it passes through the radius sections of the wellbore during horizontal drilling of an inclined directional well.

Due to the peculiarities of the operation of the gyroscopic mechanisms of screw hydraulic machines, an increased amount of heat is generated and stored at the edges of the elastomer plate from the action of the tilting rotor moments during its rotor planetary rotation inside the teeth of the stator lining of the elastomer at maximum power.

As a result, the profile center becomes less flexible (brittle and brittle), the mechanical properties of the elastomer, for example, rubber, significantly deteriorate in these areas, and the pressure acting in the chambers between the rotor and the stator may exceed the shear strength of the elastomer, and the tops of the teeth in the plate is deformed or detached from the case, thus reducing the possibility of increasing the maximum power, the torque on the output shaft in the mode of maximum power and fatigue endurance (resource) of the elastomer plate - ie less than 100 thousand cycles.

As a result, the properties of the elastomer in the structure, for example, fatigue endurance under alternating bending with rotation (GOST 10952-75), permanent deformation and fatigue endurance under repeated compression (GOST 20418-75), the temperature limit of brittleness (GOST 7912-74) are not provided, abrasion when sliding (GOST 426-77).

Another disadvantage of the known construction is the incomplete possibility of increasing reliability and resource by providing equal strength and tight threaded connections of the stator tubular housing with a sub and / or adapter under conditions of intense friction and rotation in the well bore, using hydraulic jars in the drill string, with shock loads and shock pulses from jars, as well as relaxation of tensile stresses in a curved string of drill pipes, in which a hydraulic stator is installed downhole motor.

The mentioned disadvantage of the known construction is due to the increased rigidity of the tubular body when used in a hydraulic downhole motor, essentially a large value of the bending stress ratio (Stress ratio, the ratio of the varying voltage amplitude to the average voltage) at the junction of the threaded connections of the tubular body with the sub and / or an adapter equal to 7 ÷ 9, as well as a high probability of cracking on the threads and breakage of the threaded connections of the tubular body when using a bottomhole a motor driven horizontal BHA, in areas changes downhole curvature, preferably a maximum power mode.

Due to the increased rigidity of the stator tubular body, it is not fully possible to improve the accuracy of penetration of inclined and horizontal wells, increase the rate of set of curvature parameters of the wells, as well as improve the permeability reduce the resistance and stress in the layout of the bottom of the drill string due to the bending of the tubular body of the downhole motor as it passes through the radius sections of the wellbore, which have sections of small and medium radius 30 ÷ 300 m, under conditions of intense friction in the wellbore.

As a result, the required interval of wells cannot be completed until the end, for example, in wells, in the drilling interval of 2500 ÷ 3500 m, having lateral horizontal trunks in the interval of 750 ÷ 1500 m, while the time between failures does not increase, the significant economic advantages of the known designs.

Closest to the claimed design is the stator screw gyratory hydraulic machines, for example, a motor for rotating the rotor from the pumping fluid supply or a pump for feeding fluid due to the rotation of the rotor, containing a tubular body with an inner surface made in the form of a helicoid with internal helical teeth, on each edge of the tubular body is made of internal thread, as well as containing an elastomer lining fixed in the tubular body, adjacent to the inner surface of the tubular body The lining of the elastomer is made with internal helical teeth and coincides in shape with the internal helical teeth in a tubular body, and the lining thickness is maximal on the teeth radially inward, while in the tubular body the maximum thickness of the lining of elastomer along the hollows of its inner screw surface, located at the maximum radial distance, equal to half the height of its internal helical teeth, and the minimum wall thickness of the tubular body along the radially outward outward its inner screw surface is equal to the height of the internal helical teeth in an elastomer lining, while the stator contains in the downstream part of the tubular body a damper cavity located downstream from the edge of the internal helical teeth in the tubular body directed against the flow, made in the form of an annular grooves inside the tubular body adjacent to the side surfaces of the internal helical teeth of the tubular body formed by said annular groove, and the lining of the elastomer contains The cushioned damper cavity is an input elastomer damper with its own internal helical teeth adjacent to the internal helical teeth of an elastomer plate, adjacent to the surface of the annular groove inside the tubular body and the lateral surfaces of the internal helical teeth of the tubular body formed by the said annular groove, with the possibility of bonding with the helical ring elastomer, as well as with an annular groove inside the tubular body and the lateral surfaces of the internal helical teeth of the tubular body, The annular groove, the minimum distance from the upstream edge of the internal helical teeth in the downstream part of the tubular body to the inlet edge of the inlet damper, is equal to the thickness of the inlet damper from the elastomer on its internal helical teeth radially inward, while downstream from the edge of the internal helical teeth into the downstream part of the tubular body, the elastomer plate contains an output damper of elastomer with its own internal screw teeth adjacent to the inner helical teeth of the elastomer plate, adjacent to the inner surface of the downstream part of the tubular body with the possibility of bonding with the plate of elastomer and the inner surface of the downstream part of the tubular body, with the minimum thickness of the inlet and outlet dampers of the elastomer along the hollows their internal helical teeth, located at the maximum radial distance, equal to the thickness of the lining of the elastomer on its teeth, radially directed inward (RU 2652725 C1 28.04.2018).

The main advantages of the famous stator with the same thickness of the elastomer plate (R-Wall):

- increases the load capacity of the stator, reduced hysteresis losses in the plate, increased energy performance and the braking torque of the motor section, which eliminates the likelihood of engine braking when the load changes and increases the manageability of drilling;

- the amount of generated and stored heat is reduced, the tension in the rotor-stator joint connection is less dependent on the temperature and destruction ("swelling") of the elastomer, high energy characteristics are provided in an increased interval of well depth, oil-based drilling fluids;

- Improved energy characteristics of the engine make it possible to effectively use it with PDC bits (Polycrystalline Diamond Compakt) with polycrystalline diamonds;

- at the expense of a smaller thickness of the elastomer, if the pieces of the plate are torn off, no blockage of the drilling holes of the bit occurs, as a result, the required interval of the well can be completed completely, the time between failures increases (Drilling and Oil Magazine, 11/2014, p. 56 ÷ 59) .

There is a known schedule for the development of Radius-Service engines, part of Schlumberger, who worked with StingBlade bits (Fig. 6). The data are presented for a size of 172 mm, the drilling interval reached 2000 m. Analyzing it, one can easily notice that 200 hours does not pose a problem even for standard Radius-Service engines. Journal "Drilling and Oil", No. 4, 2018, Gumich DP et al., "Drilling in one flight ...".

The main defects that reduce the reliability and life of a well-known downhole motor, in which the well-known stator is made with the same thickness of an elastomer plate (R-Wall): cracking of an elastomer (rubber) plate from the fluid outlet (drilling mud), detachment of an elastomer plate ( rubber) from the fluid outlet side, as well as tearing out of pieces of elastomer (rubber) lining in the downstream part of the lining of elastomer in the stator in tense working conditions (when drilling in hard rocks): between the rotor and the lining of the tubular body of the necessary tension, the contact pressure is 2.5 ÷ 3 MPa, the sliding speed is 0.5 ÷ 2.5 m / s, the hydrostatic pressure can reach 50 MPa, and the torque on the output shaft in maximum power mode can reach 30 kNm, and in conditions of high turbulence of the drilling fluid, which has a density of up to 1500 kg / m ³ , contains up to 2% of sand and up to 5% of oil products, which leads to cessation of circulation, while the main reason for the failure in the layout of the bottom of the drill string (BHA) in the cat Roy set the motor unit with the spindle and chisel - "tire in the bit."

Due to the peculiarities of the work of the gyroscopic mechanisms of screw hydraulic machines on the edges of the elastomer plate, an increased amount of heat is generated and stored from the action of the tilting moments of the rotor during its planetary-rotary rotation inside the teeth of the stator lining of the elastomer in maximum power mode.

As a result, the profile center becomes less flexible (brittle and brittle), the mechanical properties of the elastomer, for example, rubber, significantly deteriorate in these areas, and the pressure acting in the chambers between the rotor and the stator may exceed the shear strength of the elastomer, and the tops of the teeth in the plate is deformed or detached from the case, thus reducing the possibility of increasing the maximum power, the torque on the output shaft in the mode of maximum power and fatigue endurance (resource) of the elastomer plate - ie less than 100 thousand cycles.

As a result, the properties of the elastomer in the structure, for example, fatigue endurance under alternating bending with rotation (GOST 10952-75), permanent deformation and fatigue endurance under repeated compression (GOST 20418-75), the temperature limit of brittleness (GOST 7912-74) are not provided, abrasion when sliding (GOST 426-77).

Another disadvantage of the known design is the incomplete possibility of increasing reliability and service life by providing equal strength and tight threaded connections in the output part of the tubular body with the sub and / or adapter in the aforementioned difficult conditions of drilling bent wells in hard rocks causing high operating pressure drops, internal heat generation in the material of the housing plate, braking of the working pair during operation, high tension in the working pair, as well as under conditions of intense friction and rotation in the wellbore using the drill string hydraulic jars, shock-loads and shock pulses from the jars and upon relaxation of the tensile stress at a bent drill string, wherein a mud motor is mounted.

The mentioned disadvantage of the known construction is due to the increased rigidity of the output part of the tubular body when used in a hydraulic downhole motor, essentially a large value of the bending stress ratio (Stress ratio, the ratio of the varying voltage amplitude to the average voltage) at the junction of the threaded connections of the tubular body with the sub and / or adapter, equal to 7 ÷ 9, as well as a high probability of cracking on the threads and breakage of the threaded connection in the output part of the tubular cable Pusa using downhole motor driven horizontal in the bottom hole assembly, the areas changing downhole curvature, preferably a maximum power mode.

Due to the increased rigidity in the output part of the tubular body of the downhole motor, it is not fully possible to improve the accuracy of penetration of inclined and horizontal wells, increase the tempo of the set of curvature parameters of the wells, and also improve the permeability reduce the resistance and stress in the layout of the bottom of the drill string due to the bending of the tubular body of the downhole motor as it passes through the radius sections of the wellbore, which have sections of small and medium radius 30 ÷ 300 m, under conditions of intense friction in the wellbore.

As a result, the required interval of wells cannot be completed until the end, for example, in wells, in the drilling interval of 2500 ÷ 3500 m, with lateral horizontal trunks in the interval of 750 ÷ 1500 m, while the increase in time to failure is not ensured, significant economic advantages are not provided known designs.

The technical result, which is provided by the invention, is to increase the reliability and service life of a hydraulic downhole motor for drilling oil wells, in which the tubular stator housing is made with a uniform thickness of an elastomer plate (R-Wall) by increasing fatigue endurance, abrasion resistance, elasticity and tightness seals of the working pair: rotor-lining of elastomer in the stator, preventing cracking, delamination and tearing of pieces of the lining of elastomer into the downstream part of the body and the stator due to the execution in the downstream part of the housing damping cavity located upstream from the edge of the internal screw teeth in the housing, directed downstream, made in the form of an annular groove inside the housing adjacent to the side surfaces of the internal helical teeth of the housing formed by the said annular groove, as well as the execution of the output damper of elastomer with its own internal helical teeth adjacent to the internal helical teeth of the lining of the elastomer, and placement of the output a damper in said damping cavity formed by said annular groove, with the possibility of bonding with an elastomer lining, as well as with an annular groove inside the housing and side surfaces of the internal helical teeth of the housing formed by said annular groove.

Another technical result, which is provided by the invention, is to improve the accuracy of penetration of inclined and horizontal intervals of the wells, to increase the rate of the set of parameters of the curvature of the wells, as well as to improve the permeability, i.e. in reducing the resistance and stress in the layout of the bottom of the drill string when used in a hydraulic downhole motor by reducing the rigidity of the downstream part of the body, essentially due to the bend of the body when passing through the radius of the wellbore under conditions of intense friction along the wellbore, as well as reducing the probability of formation of fatigue cracks along the edges of the hull during resource development.

The essence of the technical solution lies in the fact that in the stator a screw gyratory hydraulic machine comprising a tubular body with an inner surface made in the form of a helicoid with internal helical teeth, an internal thread is made on each edge of the tubular body, as well as containing an elastomer plate fixed in the tubular body, adjacent to the inner surface of the tubular body, the lining of the elastomer is made with internal helical teeth and coincides in shape with the internal helical teeth in the tubular ohm body, and the thickness of the lining is maximum on the teeth, radially directed inward, while in a tubular body the maximum thickness of the lining of the elastomer along the cavities of its inner screw surface, located at the maximum radial distance, is equal to half the height of its internal helical teeth, and the minimum wall thickness tubular body along radially outward depressions of its inner screw surface is equal to the height of the internal helical teeth in the lining of elastomer, and also containing in downstream part of the tubular body damping cavity located downstream from the edge of the internal helical teeth in the tubular body, directed against the flow, made in the form of an annular groove inside the tubular body, adjacent to the lateral surfaces of the internal helical teeth of the tubular body, formed by the said annular groove, and the lining of the elastomer contains in the above-mentioned damper cavity the input damper of elastomer with its own internal helical teeth adjacent to the internal wines New teeth of an elastomer plate adjacent to the annular groove surface inside the tubular body and side surfaces of the internal helical teeth of the tubular body formed by said annular groove with the possibility of bonding with an elastomer plate, as well as with an annular groove inside the tubular body and the lateral surfaces of the internal helical teeth a tubular body formed by said annular groove, the minimum distance from the anti-flow edge of the internal screw teeth According to the invention, according to the invention, in the downstream portion of the tubular body, in the downstream part of the tubular body to the input edge of the inlet damper, the thickness of the inlet outlet of the elastomer on its inner helical teeth, radially inward helical teeth in the tubular body, directed downstream, made in the form of an annular groove inside the tubular body, adjacent to the lateral surfaces of the internal helical teeth of the tubing body formed by the annular groove, and the output damper of the elastomer is made with its own internal helical teeth adjacent to the internal helical teeth of the elastomer plate, and placed in the said damper cavity formed by the said annular groove, with the possibility of bonding with an elastomer lining, also with an annular groove inside the tubular body and the lateral surfaces of the internal helical teeth of the tubular body formed by said annular groove, wherein the min The distance from the downstream edge of the internal screw teeth in the downstream part of the tubular body to the output edge of the output damper is equal to the thickness of the output damper from the elastomer on its internal helical teeth radially inward.

The stator of the screw gyratory hydraulic machine contains in the downstream part of the tubular body a belt of reduced rigidity characterized by making the wall of the tubular body of reduced thickness located between the edge of the inner helical teeth of the tubular body directed against the flow and the full last turn of the internal thread in the downstream part of the tubular body , and in the downstream part of the tubular body contains a belt of reduced rigidity, characterized by the implementation of the wall of the tubular body of the mind The thickness is located between the edge of the internal helical teeth of the tubular body, directed downstream, and the full last turn of the internal thread in the downstream part of the tubular body, while the ratio of the reduced wall thickness of the tubular body to the downstream part of the tubular body, as well as in the outgoing downstream part of the tubular body to the outer diameter of the tubular body is 0.065 + 0.095.

Execution of the stator of the screw gyratory hydraulic machine so that it contains in the downstream part of the tubular body a damper cavity located upstream from the edge of the internal helical teeth in the tubular body, directed downstream, made in the form of an annular groove inside the tubular body adjacent to the side the surfaces of the internal helical teeth of the tubular body formed by said annular groove, and the output damper of the elastomer is made with its own internal helical teeth, Snapping to the inner screw teeth of an elastomer plate, and placed in said damper cavity formed by said annular groove, with the possibility of bonding with elastomer plate, as well as with an annular groove inside the tubular body and lateral surfaces of the internal helical teeth of the tubular body formed by the said annular groove , while the minimum distance from the downstream edge of the internal screw teeth in the downstream part of the tubular body to the output edge of you one damper, equal to the thickness of the output damper of elastomer on its internal helical teeth, radially inward, improves fatigue endurance, abrasion resistance, elasticity and tightness of the working pair seal: rotor-lining of elastomer in the stator by preventing cracking, peeling and tearing pieces plates of elastomer in the downstream of the fluid part of the plate of elastomer in the stator, as a result, provides increased resource and reliability of the stator screw her said secondary hydraulic machine using a mud motor for drilling oil and gas wells under conditions of high turbulence mud, which has a density up to 1500 kg / m ^3, contains up to 2% of sand and 5% oil, by preventing clogging of the wash assembly of the drill bit essentially preventing the main failure of the bottom hole assembly (BHA) layout during drilling for the reason - “rubber in bit”, as a result, the required interval of the well can be completed to the end, increases TKA failures, provides substantial economic advantages of the claimed design.

Execution of the stator of the screw gyratory hydraulic machine in such a way that it contains in the downstream part of the tubular body a belt of reduced rigidity, characterized by making the wall of the tubular body of reduced thickness located between the edge of the internal helical teeth of the tubular body, directed against the flow, and a full last turn of the internal thread during the downstream part of the tubular body, and the downstream part of the tubular body contains a belt of reduced rigidity, characterized by a reduced thickness, located between the edge of the internal helical teeth of the tubular body, directed downstream, and a full last coil of the internal thread in the downstream part of the tubular body, wherein the ratio of the reduced wall thickness of the tubular body to the downstream part of the tubular body, as well as in the downstream part of the tubular body to the outer diameter of the tubular body is 0.065 + 0.095, it improves the accuracy of penetration of inclined and horizontal wells in, increasing the rate of set of parameters of the curvature of the wells, as well as improving permeability, i.e. reducing the resistance and stress in the bottom hole assembly when used in a hydraulic downhole motor, essentially by bending the tubular body as it passes through the radius sections of the wellbore under conditions of intense friction in the wellbore, as well as reducing the likelihood of fatigue cracks forming along the edges of the tubular body when time resource.

Below is the best version of the stator with the same thickness of the elastomer plate (R-Wall) of the motor section of the DRU2-172 PC screw-driven gerotor hydraulic motor for oil drilling.

FIG. 1 shows a longitudinal section of the stator of a screw gerotor hydraulic motor.

FIG. 2 shows section A-A in FIG. 1 across the downstream part of the tubular body, the number of helical teeth of the body is 7.

FIG. 3 shows a section BB in FIG. 1 across the elastomer inlet damper in the damper cavity in the downstream part of the tubular body, the number of helical teeth of the inlet damper is 7.

FIG. 4 shows a section B-B in FIG. 1 across the tubular body with internal helical teeth and an elastomer lining, the number of helical teeth of the lining is 7.

FIG. 5 shows a section of YYY in FIG. 1 across the output damper of elastomer in the damper cavity in the downstream part of the tubular body, the number of helical teeth of the output damper is 7.

FIG. 6 shows a section dd in fig. 1 across the downstream part of the tubular body, the number of helical teeth of the body is 7.

FIG. Figure 7 shows a longitudinal section of the motor section, including a rotor mounted inside the inlet damper, lining and outlet damper, all of elastomer, inside the tubular body.

FIG. 8 shows section EE of FIG. 7 across the body of the motor section, which includes an input damper of elastomer and a rotor, the ratio of the number of teeth of the rotor-input damper is 6/7.

FIG. 9 shows a section of an Ж-Ж in FIG. 7 across the motor section, including the stator with an elastomer lining and the rotor, the ratio of the number of teeth of the rotor lining is 6/7.

FIG. 10 shows the section AND-AND in FIG. 7 across the body of the motor section, which includes an output damper of elastomer and a rotor, the ratio of the number of teeth of the rotor-output damper is 6/7.

The stator of the screw gyratory hydraulic machine comprises a tubular body 1 with an inner surface 2, made in the form of a helicoid, essentially with internal helical teeth 3, an inner conical pipe thread 6, for example, RKT, is made on the edge 5 of the tubular body 1 along the fluid inlet 4. 154 × 6.35 × 1: 9.6 STP 001-2007, on the outgoing fluid flow 4 edge 7 of the tubular body 1 there is an internal conical pipe thread 8, for example, РКТ154 × 6.35 × 1: 9.6 STP 001 -2007, and also contains fastened in a tubular body 1 facing 9 of elastomer, on Example, rubber stamps R1 (DE), adjacent to the inner surface 2 of the tubular body 1, while the lining 9 of elastomer is made with internal helical teeth 10 and coincides in shape with the internal helical teeth 3 in the tubular body 1, and thickness 11 of the lining 9 is maximal on its teeth 10, which are radially inward, as compared with the thickness of 12 cavities 13 along the inner screw surface 14 of said lining 9, is shown in FIG. 1, 2.4.

In the tubular body 1, the maximum thickness 12 of the lining 9 of elastomer along the cavities 13 of its inner screw surface 14, located at the maximum radial distance 15, is equal to half the height 16 of its internal helical teeth 10, while the minimum thickness 17 of the wall of the tubular body 1 along radially outwards the depressions 18 of its inner screw surface 2 are equal to the height 16 of the internal helical teeth 10 in the lining 9 of elastomer, shown in FIG. 1, 2, 4.

The stator contains in the upstream fluid 4 (drilling mud) part 5 inside the tubular body 1 a damper cavity 19 located downstream 4 from the edge 20 of the internal helical teeth 3 of the tubular body 1, directed against the stream 4, made in the form of an annular groove 21 inside the tubular body 1 adjacent to the side surfaces 22 and 23 of the internal helical teeth 3 of the tubular body 1 formed by said annular groove 21 is shown in FIG. 12.

Lining 9 of elastomer contains in the above-mentioned damper cavity 19 an inlet damper 24 made of elastomer with its own internal helical teeth 25 adjacent to internal helical teeth 10 of the lining 9 of elastomer, adjacent to the surface 21 of the damper cavity 19 inside the downstream 4 part 5 of the tubular body 1 , with the possibility of bonding with the lining 9 of elastomer, as well as with the surface of the annular groove 21 and the side surfaces, respectively, 22 and 23 of the internal screw teeth 3 of the tubular body 1, formed mentioned to An annular groove 21, shown in FIG. 1, 2, 3, 4.

The minimum distance 26 from the edge 20 of the internal helical teeth 3 in the downstream 4 part 5 of the tubular body 1 facing upstream 4 to the input edge 27 of the input damper 24 of elastomer is equal to the thickness 28 of the input damper 24 of elastomer on its internal helical teeth 25 radially inward, depicted in FIG. 1, 2, 3, is shown in FIG. 1, 2, 3, 4.

The stator contains in the downstream fluid 4 (drilling mud) part 7 of the tubular body 1 a damper cavity 29 located upstream of the fluid 4 from the edge 30 of the internal helical teeth 3 in the tubular body 1 directed along the fluid 4 An annular groove 31 inside the tubular body 1 adjacent to the side surfaces 32 and 33 of the internal helical teeth 3 of the tubular body 1 formed by the annular groove 31 is shown in FIG. 1, 4, 5, 6.

Lining 9 of elastomer contains in the above-mentioned damper cavity 29 output damper 34 made of elastomer with its own internal helical teeth 35 adjacent to internal helical teeth 10 of lining 9 of elastomer, adjacent to the surface 29 of the annular groove 31 inside the tubular body 1 and the lateral surfaces 32, 33 internal helical teeth 3 of the tubular body 1 formed by said annular groove 31, with the possibility of fastening with the lining 9 of elastomer, as well as with the annular groove 31 inside the tubular body 1 and lateral points The surfaces 32, 33 of the internal helical teeth 3 of the tubular body 1 formed by said annular groove 31 are shown in FIG. 1, 4, 5, 6.

The minimum distance 36 from the fluid direction 4 of the edge 30 of the internal helical teeth 3 in the downstream fluid 4 of part 7 of the tubular body 1 to the output edge 37 of the output damper 34 is equal to the thickness 38 of the output damper 34 of elastomer on its internal helical teeth 35 radially inward, depicted in FIG. 1, 4, 5, 6.

The stator contains in the inlet fluid flow 4 part 5 of the tubular body 1 belt 39 reduced stiffness, characterized by the implementation of the wall 40 of the tubular body 1 of reduced thickness 41 located between the edge 20 of the internal helical teeth 3 of the tubular body 1 directed against the flow of the fluid 4, and the complete last turn 42 of the internal thread 6 in the fluid inlet 4 of the part 5 of the tubular body 1 is shown in FIG. 12.

In the downstream fluid 4 part 7 of the tubular body 1, the stator includes a belt 43 of reduced rigidity characterized by making the wall 44 of the tubular body 1 of a reduced thickness 45, located between the edge 30 of the internal helical teeth 3 of the tubular body 1, directed along the fluid flow 4, and the complete last turn 46 of the internal thread 8 into the downstream fluid 4 part 7 of the tubular body 1 is shown in FIG. sixteen.

The ratio of the reduced thickness 41 of the wall 40 of the tubular body 1 in the fluid inlet 4 of part 5 of the tubular body 1, as well as the ratio of the reduced thickness 45 of the wall 44 of the tubular body 1 to the output of fluid 4 of part 7 of the tubular body 1 to the outer diameter 47 of the tubular housing 1 is 0.065 ÷ 0.095, shown in FIG. 1, 2, 6.

A stator with a uniform thickness of the elastomer plate 9 (R-Wall) is included in the module of the motor section of a downhole motor for drilling oil wells, including a spindle section, a propeller shaft, a regulator of the skew angle between the motor and spindle sections, and a chisel (not shown) with This part of the motor section includes a rotor 48 having helical teeth 49, the number of teeth 49 of the rotor 48 is one less than the number of teeth 10 of the facing 9 of elastomer, and one less than the number of teeth 25 of the input damper 24 of elastomer, as well as one less than the number of teeth 35 of the output damper 34 of elastomer, while the ratio of the number of teeth 49 of the rotor 48 to the number of teeth 25 of the facing 9 of elastomer, as well as the number of teeth 25 of the input damper 24 of elastomer, as well as the number of teeth 35 of the output damper 24 of elastomer is 6/7, while pos. 50 - the central longitudinal axis of the rotor 48, pos. 51 is a central longitudinal axis of the lining 9 of elastomer, fixed inside the tubular body 1, as well as the input damper 24 of elastomer, as well as the output damper 34 of elastomer, with pos. 52 shows the eccentricity value of the rotor 48 mounted in the lining 9 of elastomer inside the tubular body 1, bonded to the inner surface of the tubular body 1, and also installed in the inlet damper 24 of elastomer, as well as mounted in the output damper 34 of elastomer, shown in FIG. 1, 3, 5, 7, 8, 9, 10.

The hardness of the sheath 9 of elastomer, as well as the input and output ring dampers, respectively, 24 and 34, for example, from rubber brand R1 (DE), is 77 ± 3 units. Shor A.

In addition, pos. 53 - multiple spiral chambers between the teeth 49 of the rotor 48 and the teeth 25 of the input damper 24 of the elastomer, pos. 54 - multiple screw chambers between the teeth 49 of the rotor 48 and the teeth 10 of the facing 9 of elastomer, pos. 55 — multiple spiral chambers between the teeth 49 of the rotor 48 and the teeth 35 of the output damper 34 of elastomer are shown in FIG. 7, 8, 9, 10.

The design of the stator when it is used in a downhole screw motor for drilling oil wells works as follows: the flow of drilling fluid 4 under pressure, for example, 25 + 35 MPa through the string of drill pipes is fed into multiple spiral chambers 53 between the teeth 49 of the rotor 48 and the teeth 25 of the inlet damper 24 from the elastomer into the downstream fluid - drilling mud 4 of part 5 of the tubular body 1, then fed into multiple spiral chambers 54 between the teeth 49 of the rotor 48 and the teeth 25 of the cover 9 from the elastomer fixed inside the pipe of the upper body 1, then fed into multiple helical chambers 55 between the teeth 49 of the rotor 48 and the teeth 35 of the output damper 34 into the downstream fluid 4 of part 7 of the tubular body 1, forms an area of high pressure and torque from the hydraulic forces that leads to the planetary -rotor rotation of the rotor 48 inside the input damper 24 of elastomer in the input stream 4 of the fluid - the drilling fluid of part 5 of the tubular body 1, lining 9 of elastomer, fixed in the tubular body 1, and the output damper 34 of el Stomer with internal helical teeth 35 to the output 4 downstream portion 7 of the tubular body 1.

Multiple screw chambers 53 between the teeth 49 of the rotor 48 and the teeth 25 of the inlet damper 24 from the elastomer into the fluid inlet - drilling mud 4 of part 5 of the tubular body 1, multiple-thread screw chambers 54 between the teeth 49 of the rotor 48 and the teeth 25 of the elastomer plate 9 of the elastomer, fixed inside the tubular body 1, as well as multiple helical chambers 55 between the teeth 49 of the rotor 48 and the teeth 35 of the output damper 34 in the downstream fluid 4 of the part 7 of the tubular body 1 have a variable volume and periodically move along the flow fluid - drilling fluid 4, which has a density up to 1500 kg / m ^3, contains up to 2% of sand and 5% mineral oil.

The planetary rotor rotation of the rotor 48 inside the inlet damper 24 of elastomer in the fluid inlet - drilling mud 4 of part 5 of the tubular body 1, inside the teeth 25 of the facing 9 of elastomer, fixed inside the tubular body 1, and also inside the teeth 35 of the output damper 34 in the downstream fluid 4, part 7 of the tubular body 1 transmits torque (in the opposite direction) through the drive (cardan) shaft, the shaft of the spindle section to the bit fixed in the coupling thread of the shaft of the spindle section (not conjugated), carrying out drilling directional and horizontal wells.

In the maximum power mode, the frequency of rotation of the shaft of the spindle section and the bit is, for example, (1.8 ÷ 2.5) s ^-1 ; the moment of force on the shaft of the spindle section is (9 ÷ 14) kN⋅m; the differential pressure (inter-turn, on the teeth of the lining of elastomer in the housing 1) in the mode of maximum power is 17 ÷ 28 MPa; maximum axial load (per bit) is 250 kN.

The helical teeth 25 of the inlet damper 24 of elastomer in the upstream fluid 4 of the drilling fluid of part 5 of the tubular body 1, the helical teeth 25 of the elastomer plate fixed inside the tubular body 1, and also the helical teeth 35 of the outlet damper 34 in the outlet of the stream 4 Fluid part 7 of the tubular body 1 is subjected to complex deformation and bending during the planetary-rotary rotation of the rotor 48 inside the input damper 24 of the elastomer in the input stream 4 of the fluid - drilling mud part 5 of the tubular body 1, inside bkladki 9 of elastomer fixed in the tubular housing 1, as well as within the outlet damper 34 of elastomer with internal helical teeth 35 to the output 4 downstream portion 7 of the tubular body 1.

In the inventive design due to the fact that the stator contains in the downstream fluid 4 (drilling mud) part 7 of the tubular body 1 a damper cavity 29 located upstream of the fluid 4 from the edge 30 of the internal helical teeth 3 in the tubular body 1 directed along the fluid flow 4, made in the form of an annular groove 31 inside the tubular body 1 adjacent to the side surfaces 32 and 33 of the internal helical teeth 3 of the tubular body 1 formed by said annular groove 31, while the cover 9 of elastomer with in the damper cavity 29, the output damper 34 is made of elastomer with its own internal helical teeth 35 adjacent to the internal helical teeth 10 of the elastomer facing 9 adjacent to the surface 29 of the annular groove 31 inside the tubular body 1 and the lateral surfaces 32, 33 of the internal helical teeth 3 tubular body 1 formed by said annular groove 31, with the possibility of bonding with the lining 9 of elastomer, as well as with the annular groove 31 inside the tubular body 1 and the side surfaces 32, 33 of the inner their helical teeth 3 of the tubular body 1 formed by said annular groove 31, the minimum distance 36 from the fluid direction 4 of the edge 30 of the inner helical teeth 3 in the downstream fluid 4 of part 7 of the tubular body 1 to the output edge 37 of the output damper 34 equal to the thickness 38 of the output damper 34 of elastomer on its internal helical teeth 35, radially inward, zones of increased shear strength are provided, a decrease in temperature gradient during the separation of those plate inside the material of the teeth of elastomer, improves the removal of internal heat from the plate 9 of elastomer, as well as from the output damper 30 from the elastomer to the fluid flow 4 inside the tubular body 1, as well as through the walls of the tubular body 1 to the drilling fluid from the outer side of the tubular body 1 (annulus), the flow of which is directed from the bottom (from the bit) to the wellhead.

This increases the elastic strength properties of the elastomer in the design: fatigue endurance with alternating bending with rotation (GOST 10952-75), residual deformation and fatigue endurance under repeated compression (GOST 20418-75), the temperature limit of fragility (GOST 7912-74), abrasion with slip (GOST 426-77), as a result, the likelihood of cracking, detachment and tearing of pieces of an elastomer plate in the inlet and downstream parts of an elastomer plate in the stator is reduced; ovogo bit is eliminated primary failure the bottom hole assembly (BHA) during drilling due to - "in the bit tires", thereby wellbore interval can be requested until the end doburen increases MTBF provide significant economic benefits of the claimed design.

In the inventive design due to the fact that the stator contains 4 parts 5 of the tubular body 1 in the fluid inlet stream 1 belt 39 of reduced rigidity, characterized by making the wall 40 of the tubular body 1 of reduced thickness 41 located between the edge 20 of the internal helical teeth 3 of the tubular body 1, directed against the fluid flow 4, and a full last turn 42 of the internal thread 6 in the fluid inlet 4 of the part 5 of the tubular body 1, while in the fluid outlet of the 4 of the part 7 of the tubular body 1 st Ator contains a belt of reduced rigidity 43, characterized by making the wall 44 of the tubular body 1 of reduced thickness 45, located between the edge 30 of the internal helical teeth 3 of the tubular body 1 directed along the flow of the fluid 4, and the full last turn 46 of the internal thread 8 into the outgoing fluid medium 4 of the part 7 of the tubular body 1, and the ratio of the reduced thickness 41 of the wall 40 of the tubular body 1 in the fluid inlet 4 of the part 5 of the tubular body 1, as well as the ratio of the reduced thickness 45 of the wall 44 of pipes This body 1 in the downstream fluid 4 of part 7 of the tubular body 1 to the outer diameter 47 of the tubular body 1 is 0.065 ÷ 0.095, improving the accuracy of penetrating inclined and horizontal wells, increasing the rate of curvature parameters set, and improving the permeability, t. e. reducing the resistance and stresses in the bottom hole assembly when used in a hydraulic downhole motor by reducing the stiffness of the tubular body, which ensures bending of the tubular stator body as it passes through the radius of the borehole, having small and medium radius of 30 ÷ 300 m, under conditions of intense friction in the wellbore.

The invention improves the reliability and resource when used in a hydraulic downhole motor for drilling bent wells by increasing fatigue endurance, abrasion resistance, elasticity and tightness of the seal of the working pair: rotor-lining of elastomer in the stator by preventing cracking, delamination and tearing of pieces of the elastomer lining into stator, due to this, blockage of the drilling bit of the drill bit is prevented, as a result, the required interval of the well can be completed completely, increases Xia time to failure, the economic advantages of the claimed design.

The invention, when used in a hydraulic downhole motor, also improves the accuracy of penetration of inclined and horizontal wells, the rate of set of parameters of the curvature of the wells, and also improves the permeability, i.e. reduces the resistance and stress in the bottom hole assembly by reducing the rigidity of the body, ensuring the body bends when passing through the radius of the wellbore under conditions of intense friction along the well bore, and also reduces the likelihood of fatigue cracks forming at the edges of the body during life.

Claims (2)

1. The stator of the screw gyratory hydraulic machine, comprising a tubular body with an inner surface made in the form of a helicoid with internal helical teeth, on each edge of the tubular body an internal thread is made, as well as containing an elastomer plate fixed in the tubular body, adjacent to the inner surface of the tubular body, the lining of the elastomer is made with internal helical teeth and coincides in shape with the internal helical teeth in a tubular body, and the thickness of the lining is maximum teeth indented radially inward, while in a tubular body the maximum thickness of the lining of elastomer along the cavities of its inner screw surface located at the maximum radial distance is equal to half the height of its internal helical teeth, and the minimum thickness of the wall of the tubular body along radially outwards of the cavities of it the inner screw surface is equal to the height of the internal helical teeth in the lining of elastomer, and also containing in the downstream part of the tubular body a damper a cavity located downstream from the edge of the internal helical teeth in the tubular body, directed against the flow, made in the form of an annular groove inside the tubular body adjacent to the side surfaces of the internal helical teeth of the tubular body formed by said annular groove, and the elastomer lining contains in damper cavity input elastomer damper with its own internal helical teeth adjacent to the internal helical teeth of an elastomer plate adjacent to the surface the circumferential groove inside the tubular body and the lateral surfaces of the internal helical teeth of the tubular body formed by said annular groove, with the possibility of bonding with an elastomer lining, as well as with an annular groove inside the tubular body and the lateral surfaces of the internal helical teeth of the tubular body formed by the said annular groove the minimum distance from the upstream edge of the internal helical teeth in the downstream part of the tubular body to the entrance edge of the inlet damper is equal to the thickness of the inlet damper of elastomer on its internal helical teeth radially inward, characterized in that it contains in the downstream part of the tubular body a damper cavity located upstream from the edge of the internal helical teeth in the tubular body directed along the flow, made in the form of an annular groove inside the tubular body, adjacent to the side surfaces of the internal helical teeth of the tubular body, formed of the aforementioned annular groove oh, and the elastomer plate contains, in said damping cavity, an elastomer outlet damper with its own internal helical teeth adjacent to the internal helical teeth of an elastomer plate adjacent to the annular groove surface inside the tubular body and the lateral surfaces of the internal helical teeth of the tubular body formed by the annular groove groove, with the possibility of bonding with the lining of the elastomer, as well as with an annular groove inside the tubular body and the side surfaces of the inner The screw teeth of the tubular body formed by said annular groove, wherein the minimum distance from the downstream edge of the internal screw teeth in the downstream part of the tubular body to the output edge of the output damper is equal to the thickness of the output damper of elastomer on its internal helical teeth radially inward . 2. The stator of the screw gyratory hydraulic machine according to claim 1, characterized in that it contains in the downstream part of the tubular body a belt of reduced rigidity characterized by making the wall of the tubular body reduced in thickness, located between the edge of the internal helical teeth of the tubular body directed against the flow, and full the last turn of the internal thread in the downstream part of the tubular body, and in the downstream part of the tubular body contains a belt of reduced rigidity, characterized by Tanks of the tubular body of reduced thickness, located between the edge of the internal helical teeth of the tubular body, directed downstream, and a full last coil of the internal thread in the downstream part of the tubular body, the ratio of the reduced wall thickness of the tubular body to the downstream part of the tubular body, and also in the downstream part of the tubular body to the outer diameter of the tubular body is 0.065 ÷ 0.095.

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