Multi-row ball bearing
The invention relates to the field of drilling wells for oil or gas, in particular to constructions sites downhole motors. Multi-row ball bearing consists of 12-15 rows of balls resting on the conical surface of the stator casing and the conical surface of the rotor casing. The position of each row of balls on the carriers is determined by the diametral and axial dimensions of the rotor and the stator spacer rings. The slope of the conical surfaces of the rotor casing to the plane perpendicular to the longitudinal axis of the multi-row ball bearing is selected in the range from 15 to 35°. The inclination of the tapered surfaces of the stator casing to the plane perpendicular to the longitudinal axis of the multi-row ball bearing, 5-15° more than tilt to the same plane of the conical surfaces of the rotor casing. The invention provides improved reliability of operation of downhole motors, increases the service life of their spindles. 3 Il.
The present invention relates to means used for drilling oil and gas wells, more precisely to the assemblies and parts downhole motors that cause the rotation of the drill bits, ug is (see sourceTurbine oil drilling, M. I. Guzman, Moscow, 1952, Costoptimized, pp. 55-56.). The design of this bearing was very difficult and-low-tech manufacturing, resulting not found industrial application.
The closest analogue of our invention is toBall bearing" as described by A. C. of the USSR №166627, 25.08.62. In this author's testimony described multi-row ball bearing comprising balls and thrust rings (hoops). The balls of each row bearings are enclosed between the cylindrical rotor spacer rings, which are separated from each other by a rotary thrust holder, and a cylindrical stator spacer rings, which are separated from each stator resistant casing. The difference of diameters between the outer cylindrical surface of the rotor spacer rings and the inner cylindrical surface of the stator spacer rings is equal to twice the diameter installed in between the balls. Rotor and stator resistant casing having working surfaces that come in contact with the balls, made in the form of conical surfaces inclined to the plane perpendicula and quite a large abrasive, the balls roll on persistent clips spherical track, resulting in the support is formed of an axial backlash.
The amount of backlash in 6-7 mm limit exemption resistance of the bearing, which ranges from 60-120 hours of Work multi-row ball bearing in the environment of drilling fluid characterized by a single feature, which is characteristic only of the bearings of this type.
The desire to make a ball bearing to the maximum extent lifting leads to the fact that by increasing the diameter of the balls, the designers are forced to utonet spacer rings. Today, their thickness varies from 4.7 to 5.5 mm, While the length of the contact circle (point of contact of the balls with rotor and stator thrust clips) differ by 15-20%. Consequently, the rotor thrust clip produced is always faster than the stator holder. You receive the spacer component of the axial force, which, being summarized in the course of the centrifugal force acting on each ball, more intense starts fraying stator spacer rings. Taking into account that the mounting features multi-row ball bearings in the spindles turbodrills provide their fixation in the body of the spindle axial force in the 600-800 kN tension in each of the stator igodit to their swelling and saclike in the spindle body. Or have to nederbeat support up to the maximum possible axial play, reducing their possible lifespan, or vyrisovyvat the bearing housing of the spindle that is not always possible. In this case, the entire spindle is turning into scrap metal.
The invention allows the release of multi-row ball bearing from wear spacer rings and thereby increase resource work supports up to 250-300 hours, as it is possible to modify the bearing to the axial backlash in 10-12 mm.
The invention consists in creating multi-row ball bearing, consisting of several rows of balls, impact resistant casing, between which are mounted a rotary spacer ring; a stator resistant casing, between which are mounted a stator spacer rings, while the difference between the inner diameter of the stator spacer rings and the outer diameter of the rotor spacer rings is equal to twice the diameter installed in between the balls. Each of the stator and rotor thrust cone has a conical surface in contact with the balls, and the inclination of the tapered surfaces of the stator thrust raced to the plane perpendicular to the longitudinal axis of the multi-row ball bearings, all structural performance of multi-row ball bearings downhole motors allows at least to double the exemption lifetime of their spindles.
The invention is illustrated in three figures.
In Fig.1 shows in cross section a General view of the multi-row ball bearings.
In Fig.2 shows the cross-section of one of the rotary cage multi-row ball bearings.
In Fig.3 shows the cross-section of one stator holder multi-row ball bearings.
In most cases, ball bearing consists of 12-15 rows of balls 1, which is supported on the conical surface 2 of the stator casing 3 and the conical surface 4 of the rotor casing 5. The position of each row of balls 1 on the clamps 3 and 5 is determined by the diametral and axial dimensions of the rotor 6 and the stator 7 spacer rings. The difference between the internal diameterDineach stator spacer ring 7 and an outer diameterdneach rotor spacer ring 6 is equal to twice the diameter of the ballsdW. The axial height of thehocthe rotor 6 and Satarov 1 relative to the conical surfaces 2 and 4 of the stator casing 3 and the rotor casing 5 in the range of 0.1-0.5 mm
The slope of the conical surface 4 of the rotor casing 5 to the plane perpendicular to the longitudinal axis of the multi-row ball bearing (indicated by the index of), is selected within 15-35°, depending on the overall diameter of the ball bearing and the diameter of the ballsdWinstalled in each of its rows.
The inclination of the tapered surfaces of the stator 2 of the 3 clips to the plane perpendicular to the longitudinal axis of the multi-row ball bearing (indicated by the index of), 5-15° more than tilt to the same plane of the conical surface 4 of the rotor casing 5. The difference in the angles is greater, the larger the diameter of the ballsdWinstalled in each row, multi-row ball bearings.
The WORK of the MULTI-row BALL BEARINGS IN the SPINDLE HOLE of the ENGINE
The new multi-row ball bearing is mounted on the shaft of the downhole motor as mounted serial ball bearing (nl is her section of the engine. To the shaft of the spindle is fixed a bit, and then begins the descent downhole motor to drill pipe in the wellbore drilled wells. Downhole arrangement for 8-12 m not brought tooldslaughter drilled wells, and then incorporated in the work of mud pumps. Within 10-15 minutes the new multi-row ball bearing with a minimum flow of drilling mudroll theabove the old bottom, after which the feed pump is displayed on the normal mode and begins the process rassilki, and then drilling wells.
In the process of rolling under the action of the hydraulic load on the rotary elements of the ball bearing and the corresponding reaction on its stator elements is axially production of tapered thrust surfaces of the clamps and alignment of the axial load on the rows of ball bearings. Any difference in the anglesandthe conical surfaces of the rotor 5 and the stator 3 clips multi sartory (MTBF supports, consequently, the spindle was determined only by the magnitude of the generated axial play in the bearing, that is, the axial height of her clips and backlash of the working bodies of the engine.
Multi-row ball bearing, consisting of several rows of balls, impact resistant casing, between which set rotor spacer ring, stator resistant casing, between which set of stator spacer rings, while the difference between the inner diameter of the stator spacer rings and the outer diameter of the rotor spacer rings is equal to twice the diameter of the installed between the balls, each of the stator and rotor thrust cone has a conical surface in contact with the balls, characterized in that the inclination of the tapered surfaces of the stator thrust raced to the plane perpendicular to the longitudinal axis of the multi-row ball bearing, 5-15° more than the inclination of the tapered surfaces on the same plane of the rotor thrust clips.
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.