Stage pressure turbine of the turbo-drill
(57) Abstract:The invention relates to turbine drilling of deep wells, in particular to the implementation of the turbine of the turbo-drill. Stage pressure turbine of the turbo-drill consists of a hub of the stator is pressed into it, the stator blade of the crown having an inner rim, and the chord of the blades of the stator crown is inclined to the plane perpendicular to the axis of the pressure stage of the turbine, at an angle not exceeding 50°. The inner surface of the larger diameter stator blade rounded crown radius R, whose center is the axis of the pressure stage of the turbine. Inside the hub of the stator and pressed into her shoulder crown freely inserted the rotor hub with pressed on her the rotor blade tip. Thus the chord of the rotor blades of the crown is inclined to the plane perpendicular to the axis of the pressure stage of the turbine, at an angle not less than 70°. The rotor blades of the crown have a guaranteed gap Z relative to the hub of the stator within the range of values from 0.1 to 0.2 from the radial height h3the rotor blades of the crown. The invention provides increased service life of the axial bearings of the turbo-drill and in General, increasing the turnaround is rednaznachena for drilling oil and gas wells and in a narrower division of these funds - for constructive nodes downhole motors - turbodrills, through which are driven drill bits.Analogue of the invention is the stage pressure turbine, described on page 18, Fig. 2 (see Turbine oil drilling. PP Shumilov, part I, lecture notes.Heavy industry. USSR, Moscow 1936, Leningrad).In the source describes the degree of pressure turbine having conoidal surface of the restricting blade crown of the stator, while the rotor crown made without the outer rim.This design pressure stage of the turbine has two major drawbacks: a large axial hydraulic load on the turbine rotor and the impossibility of drilling a turbodrill for drilling fluids containing an inert PlayReady filler type melkorublenyh cord fiber or plate-fish scales, which, falling in the narrow gap between the rotor blades rims and corresponding stator hub pressure stages of the turbine, one shaft of the turbo-drill.The closest analogue of the invention is a turbine is performed according to the claims of the patent of Russian Federation N 2032063 (see PP. 18 and 19). This patent describes the degree dawni pressure turbine stator of a turbo-drill. But in the mentioned patent is not resolved and is not described none of the design features that reduce to a minimum axial hydraulic load on the rotor of the mud motor and avoid zaklinsky ends of the blades of the rotor crowns inert filler. Therefore, turbodrills so far not drill into the geological sections prone to mud loss.The invention allows to drill a turbodrill in all geological formations, including those prone to partial or full acquisitions of mud, while allowing for increasing trouble-free service life of the axial bearings of the turbo-drill to significantly increase its overhaul life.The essence of our invention is to provide recolorations turbine, bezobidnoy blade crown pressure stage rotor which has a large radial clearance relative to the hub of the stator. This gap is so large that it can't wedge themselves flakes filler, washed out of him by the flow of drilling mud.All the designs of pressure turbine turbodrills increase the radial clearance blade row of the rotor relative to the ACC is of the efficiency of the turbine of the turbo-drill. In the construction of turbines with bezobidnymi blade rims rotary pressure (see nearest equivalent) under the action of centrifugal force to the slurry and the filler are displaced towards the ends of the blades get jammed and break them. When the rotor of the mud motor or jams in the stator or broken blades, falling into the lower pressure stage, break their blades, then all turbodrill turbine turns into scrap metal.In the invention the blades of the rotor crowns are profiling and installed so that the operating frequencies of the rotation shaft of the rotor of the turbo-drill the main part of the differential pressure in the turbine is implemented in the stator blade rows. Thus to the possible minimum reduced hydraulic axial load on the rotor of the turbo-drill and reduced leakage of the drilling fluid in the gaps of the rotary crowns. This fact is especially important for designs turbodrills with independent spindle axial bearing heel in each section.The invention is illustrated in three figures.In Fig. 1 shows the General layout of the pressure stage of the turbine.In Fig. 2 shows a detail of the upper crown pressure stage stator of the turbine.Inside the hub of the stator 1 and the shoulder of the crown of the stator 2 is freely inserted the rotor hub 4, which is pressed (or secured in any other appropriate way) blade crown of the rotor 5. In Fig. 1, the rotor hub 4 is based on the ring 6 (in the Assembly of the turbodrill it is not used), with which the rotor hub 4 is the actual position in which it is assembled turbodrill. The upper axial clearance is a value from 2 to 4 mm, the Lower axial clearance b is always greater than the clearance a and has a value of from 8 to 12 mm stator Vanes 7 of the crown 2 is performed in such a way that their radial height h1measured on the input side is always greater than their radial height h2measured on the output edge. The inner surface of the larger diameter of the shoulder of the crown 2 of the stator rounded with a radius "R", Zentai section of the shoulder of the crown 2 output edges of his shoulder blades. The inner rim 3 has a mainly rectangular cross-section, which in its upper part may have a smooth radius fillet.Blade crown of the rotor 5 has a radial height h3blades 8, or equal to 1 to 3 mm greater than the radial height h2the stator blades of the crown 2. Radial clearance Z of the rotor blades of the crown 5 relative to the hub 1 is well within the range of values from 0.1 to 0.2 from the radial height h3blades 8 rotary crown 5.The turbodrills relatively large diameter on the hub of the rotor 4 may be the groove 9, into which is inserted a rubber or rubber-to-metal seal 10, which may be of round, rectangular or elliptical shape.The seal 10 overlaps the gap between the rim 3 of the shoulder of the crown 2 of the stator and the rotor hub 4.The turbodrills small diameter on the hub 4, it is impossible to perform the groove 9, so on the outer surface of the hub 4 is cut fine metric thread (right screw).The stator vanes 7 of the crown 2 is performed so that the slope of the L chord 11 to the plane perpendicular to the axis of the pressure stage of the turbine, does not exceed the values in the 50o, ornago crown 5 are thus their chord 12 coincides with the target plane of the inner surface of the blades 8. When this chord 12 is inclined at an angle to a plane perpendicular to the axis of the pressure stage of the turbine, at an angle of not less than 70o. Thus the slope of the chord 11 of stator blades 7 is different from the slope of the chord 12 of the blades 8 of the rotor angle of more than 20o.The minimum gap dpbetween two adjacent blades 8 rotary crown should be not less than 11 mm, the performance blade rims 2 of the stator and 5 of the rotor allows the operating frequency range of rotation of the mud motor to actuate the main part of the pressure drop in the stator of a turbo-drill simultaneously raising to the highest possible overall efficiency of the turbine and reducing to a minimum the amount of hydraulic axial load on the axial bearings of the turbo-drill. At the same time such a performance pressure stages of the turbine allows the turbodrill properly working on solutions containing fibrous or lamellar fillers.WORKING PRESSURE STAGE OF THE TURBINE OF THE TURBO-DRILL
The flow of drilling fluid up through the stator vanes 7 of the crown 2, generates kinetic energy. When seal 10 is liquidated leak part of the solution flow rate in kolawole leakage is eliminated and the effect of "zataskivanija" filler specified in the annular channel, that is liquidated and the reason that causes Salenko rotating hub 4 rotary pressure stage of the turbine of the turbo-drill.In the absence of the hub 4, the seal 10 is trapped in the annular gap filler with a thread cut on the outer surface of the hub 4, being pushed in the axial upper interfering with a gap.The flow of drilling fluid passing through the stator blades 7 of the crown 2, flowing down over the surface formed by the radius R, deviates from the ends of the blades 8 of the rotary crown 5. At the end a sharp edge (pair of radius R and output edges of the blades 7) blade of the crown 2 is formed vortex circulation, the rotation of which is directed against clockwise movement. This vortex escapes the gap Z between the ends of the blades 8 and the corresponding wheel hub 1 stator pressure stage of the turbine). If individual particles or flakes filler and fall into the gap under the action of centrifugal force from the rotating blades 8, unlike bezobidnyh turbines with a low value of this gap, they do not get jammed rotary stage pressure turbine in the hub of the stator 1 stage pressure and flow of the solution are carried at the lower axial clearance b.M is th crown 5 (designation dpsubstantially greater than that of the turbines other structural types. This allows you to "skip" over the shoulder crowns viscous drilling fluids with a high concentration playlouder filler (filler mud to fight acquisitions drilling fluid in the wellbore). 1. Stage pressure turbine of the turbo-drill, consisting of a stator hub pressure with fixed inside the stator blade ring having an inner rim, and a rotary pressure, consisting of a hub of a rotary pressure attached to it a rotary blade crown, characterized in that the radial clearance between the ends of the rotor blades of the crown and the stator hub is well within the range of values from 0.1 to 0.2 from the radial height of the vane rotor crown.2. Stage pressure turbine of the turbo-drill performed on p. 1, characterized in that the stator blade, the crown has an inner surface with a larger diameter, described by a radius, the center of which is located from the axis of the pressure stage of the turbine.3. Stage pressure turbine of the turbo-drill performed on p. 1, characterized in that the slope of the chord of the blades of the stator crown of the NCA to the same plane at an angle of more than 20°, thus the chord of the blades of the stator crown tilted to the specified plane at an angle of not more than 50°, and the chord of the rotor blades of the crown at an angle of not less than 70°.4. Stage pressure turbine of the turbo-drill performed on p. 1, characterized in that the hub of the rotary pressure stage of the turbine has an elastic sealing contact with the inner surface of the rim of the stator blade and the crown.5. The degree of pressure of the turbo-drill performed on p. 1, characterized in that on the outer surface of the rotor hub pressure stage of the turbine is running, the screw thread.
FIELD: oil and gas extractive industry.
SUBSTANCE: device has metallic hubs of stator and rotor, wherein crowns of stator and rotor are concentrically pressed. Crowns of stator and rotor are made of durable ceramics and are additionally equipped with connections, allowing to exclude non-controlled turning of crowns in hubs and spontaneous axial displacement thereof.
EFFECT: higher reliability and efficiency.
FIELD: mining industry.
SUBSTANCE: method includes physical-chemical treatment of metallic body parts, made in form of two half-cylinders, placement of puncheon within them, preparation of fresh rubber mixture, heating press-form up to 150±2°C, with following vulcanization of rubber mixture, detaching press-form, removing puncheon and controlling manufacture. Three compounds of rubber mixture are prepared, with following calendaring thereof on shafts and preparing fresh rubber strip of each compound, 0.5-0.6 mm thick, which prior to placement of puncheon in half-cylinders is wound in halving fashion onto the latter. Of rubber strip of compound, providing for durability, inner layer of rubber winding is made, of compound strip, providing for auto-compensation of wear - middle layer, and of strip, providing for hardness of connection between resin and half-cylinders - outer layer. Each layer of rubber winding is made of thickness, determined from relation k·hw, where h - thickness of each winding layer, mm; k - coefficient, determined empirically, equal to 30-0.35 for inner layer, 0.50-0.60 for middle layer, 0.10-0.15 for outer layer; hw - total thickness of rubber mixture winding, mm. glue covering is applied to each layer and rolled under pressure. After heating of press-form, the latter is placed into one of half-cylinders. Puncheon with rubber winding is deployed and connected to second half-cylinder. After vulcanization and removal of puncheon, rubber-metallic portion of stator is fixed in body pipe.
EFFECT: higher durability and simplified maintenance.
4 cl, 2 dwg, 5 ex
FIELD: oil and gas industry.
SUBSTANCE: device has turbine module, screw gear couple, including stator and rotor, assembly for connection of rotor of screw gear couple to turbine module and spindle, according to invention, rotor of screw gear couple has pass channel, into which a valve is mounted, including locking element and saddle, while locking element is mounted on resilient element with space to saddle surface and with possible contact with saddle surface. When engine is launched whole flow of drilling mud skirts screw gear couple through pass channel in rotor and open valve, i.e. through space between locking element and saddle surface and is directed into turbine module. In face engine loads on elements of gear couple are decreased during its launch due to redistribution of flows of working liquid between screw gear couple and turbine.
EFFECT: higher reliability, higher durability.
2 cl, 3 dwg
FIELD: mechanical engineering.
SUBSTANCE: rotor axis of gear mechanism, performing a planetary movement, is displaced relatively to stator axis for distance of engagement eccentricity. As source auxiliary contour ellipse is used, while proportional coefficient k, determining radius of guiding circle, is taken equal to half necessary number of teeth z of wheel (k = z/2), optimal shape of its teeth is provided by rational combination of ellipse shape coefficient λ, equal to relation of lengths of its semi-axes and eccentricity coefficient of auxiliary contour, in form of relation of length of greater ellipse semi-axis to rolling circle radius, while inner and outer profiles are made in form of elliptic profiles from common ellipse contour.
EFFECT: simplified manufacture.
3 cl, 11 dwg
FIELD: oil and gas industry.
SUBSTANCE: roller tracks at edge inner and outer rings are made on same side, roller tracks at inner and outer rings are made with possible contact of balls with roller tracks of inner and outer rings at angle, greater than 45°, angle being formed by line, passing through points of contact of balls with roller tracks of inner and outer rings and line, perpendicular to longitudinal axis of bearing, profile of roller tracks on inner and outer rings is made from inequality condition D1 > (Din + Dout)/2, where D1 - diameter of circle passing through centers of balls in assembled bearing, Din - inner diameter of inner ring, Dout - outer diameter of outer ring, hardness of inner and outer rings being greater than 48 HRC, application point of radius of roller tracks profile on inner rings is placed in plane of stopping end of inner ring.
EFFECT: higher durability and reliability.
FIELD: oil and gas well boring equipment.
SUBSTANCE: boring rig comprises turbodrill, drill bit and reducer including several planetary mechanisms and installed in-between. Sun gears of both planetary mechanisms are secured to turbodrill rotor shaft. Carrier with plane pinion axes of upper planetary mechanism is connected to boring rig body. Ring gear is attached to upper link of drill bit. Ring gear of lower planetary mechanism is linked with plane pinion axes of upper planetary mechanism, carrier thereof is connected with lower link of drill bit.
EFFECT: increased efficiency due to increase in turbodrill rotor speed up to optimal value, reduced number of turbodrill steps and hydraulic resistance thereof, increased flushing liquid flow velocity, reduced reactive moment on turbodrill stator and pipe string.
FIELD: oil and gas well drilling equipment, particularly hydraulic downhole motors.
SUBSTANCE: device has screw bottomhole motor comprising sub and body for arranging operating tool sections. Tool sections are mating rotor and stator surfaces made in the form of multistart screw pair. Tangential current-speed and inlet drilling mud direction transducer is installed above screw pair. The transducer comprises body, retaining ring and sealing collar. Blades of the transducer are right-handed (in opposition to helical teeth of the rotor and the stator).
EFFECT: increased mechanical penetration rate due to increased load applied to drilling bit without reduction in power and shaft torque indexes.
FIELD: drilling equipment, particularly for directional drilling, namely control devices adapted to control angle and reactive moment.
SUBSTANCE: control device has hollow central member and three hollow tubular noncoaxial members connected to hollow central member. Inner member is disposed in center between the first and the second members. The first and the second members are connected with inner members by threaded connection. The first member is connected to spindle by threaded coupling, the second member is attached to engine body by threaded coupling and central member is connected to inner member by spline. Each of central member and the first member are provided with sectional contact seats located from spindle connection side, wherein a pair of sectional contact seats arranged from either sides of meridional spindle plane in drilling string curvature plane are defined between central and the first members. Sectional contact seats defined between central and the first members are spaced a distance L from the nearest edges of sectional contact seats of central and the first members along central axis of the first member. The distance L is more or equal to spindle diameter D. Angular deviation of the sectional contact seat formed in the first member from meridian spindle plane in drilling string curvature plane is oppositely directed relative reactive drilling bit moment.
EFFECT: increased stability and angle of gerotor engine deflection and increased accuracy of non-uniform well bottom zone penetration.
2 cl, 10 dwg
FIELD: well drilling equipment, particularly bearings adapted to work in abrasive medium.
SUBSTANCE: radial bearing has body and shaft, as well as thrust collars secured in the body and spring-loaded holders arranged between the shaft and the body. Inserts with conical outer surfaces are located between the holders and the shaft so that inserts cooperate with the shaft and with inner surfaces of the holders. Radial bearing is made as two oppositely arranged blocks and as compression spring inserted in-between. Each block has stop member secured in the body and made as slotted bush. Inserts are arranged in the bush and may perform displacement in radial direction. Thrust collars have conical surfaces cooperating with outer surfaces of the inserts. Angles α at apexes of the cones defined by interacted conical surfaces of bearing support inserts, thrust collars and holders are correlated with friction coefficient μ of interacted surfaces as tg(α/2)≈μ. Insert surfaces cooperating with shaft surface may have coating of elastomeric or hard-alloy material. In accordance with the second embodiment surfaces of inserts, thrust collars and holders interacting one with another may have flat contact zones, which are inclined at (α/2) angle to longitudinal shaft axis.
EFFECT: increased operational reliability of radial bearing.
6 cl, 3 dwg
FIELD: oil and gas well drilling equipment with the use of hydraulic downhole motors.
SUBSTANCE: support-and-centering member is made as metal hub with blades connected to spindle connector. Spindle connector has support cone formed on outer surface thereof and adapted to provide rigid connection with metal hub from inner surface thereof. Support cone of the connector is formed from side of conical thread connecting spindle body with connector. Spindle connector has splines to connect thereof with metal hub. Metal hub is pressed with pressing cone, retaining washer and nut from another side thereof. Metal hub may be installed concentrically or eccentrically to spindle connector axis or outer surface thereof may be differently shaped and arranged eccentrically, concentrically or obliquely with respect to spindle connector axis.
EFFECT: reduced costs of spindle usage.