Borehole helical motor
FIELD: engines and pumps.
SUBSTANCE: invention relates to borehole helical motors. This motor consists of two, tope and bottom sections. Each of the latter comprises screw working members built around multistart gerotor mechanism with internal cycloidal engagement. Spindle with output shaft runs in axial and radial bearings. Hinge joint of rotor helical working members with output shaft and fluid passages. Helical working members stator of top section is fixed at drilling string. Bottom section output shaft is coupled with rock cutting tool. Top section output shaft is rigidly coupled with bottom section helical working member stator fitted in adapter bore coupling fixed bodies of spindles and concentrically spinning in adapter radial bearing.
EFFECT: enhanced power characteristics, particularly, higher output shaft rpm.
2 cl, 5 dwg
The invention relates to the oil and gas industry, namely, engineering and technology drilling oil and gas wells using hydraulic downhole motors.
Known screw downhole motors (PDM) to drive the rock cutting tool during drilling and workover [Balenko J.F. ñ, Balenko FD, Gnoevykh A.N. Single-rotor hydraulic machines, Vol.2. - M: IDC Gazprom, 2007]. The working body of the PDM is a helical gear pair with internal cycloidal gearing consisting of a metal of the rotor and stator with elastic lining, between the helical surfaces of which are formed a working camera.
When working PDM rotor, objetivas inside the casing to the fixed stator, performs a planetary motion (rotates about its own axis, which is drawn in a figurative movement about a fixed axis motor and an output shaft connected to a rotor via a swivel, makes concentric rotation in radial bearings spindle section. The angular velocity of the rotor axis in a figurative movement in the z2times the angular velocity of the rotor in absolute motion, which corresponds to the angular velocity of the output shaft and rock cutting tool that due to the action of the inertial centrifugal forces largely determined the permissible speed PDM and limits the multiple speed, high-torque engines (z 2>5) at the level of 100-200 rpm
However, in modern drilling techniques in certain geological conditions the efficiency of the well construction can only be achieved through the use momentously type PDC bits with polycrystalline or carbide, for rational testing which is required to provide medium - and high-speed modes with speed not less than 300 rpm
When using PDM standard design specified speed can be achieved only by reducing the working volume of the engine by shifting to a screw pair with the least operating. However, the desired reduction in volume is accompanied by a decrease torque PDM that does not match the characteristics of the type PDC bits. In this regard, to create a PDM, at the same time meet the requirements of high speed and high torque, it is necessary to significantly increase the pressure drop in the working bodies, i.e. to use extra long working bodies in order to ensure the required number of contact lines separating the input and output hydraulic selected as the condition of permissible turn-to-turn pressure differential between chambers PDM. The disadvantage of this technical solution is to increase the OS is the first dimension of the PDM and the complexity of manufacturing technology extended working bodies, that adversely affects the technical-economic indicators of the PDM application.
Another possible technical solution for developing high-speed, high-torque PDM is the transition to non-standard kinematic scheme of its working bodies with additional mobility of one of the elements (rotor or stator), in which none of the elements of the screw remains stationary during the working process.
The closest technical solution adopted for the prototype, is the PDM schema with numerousin (commit portable motion of the rotor and the rotating stator, in which the bit is connected with performing the concentric rotation of the outer element of the working bodies (the stator), the teeth of which obkatyvalisj around the inner element (rotor), hinged to the end of the drill pipe string [Tiraspolsky W. Hydraulic downhole drilling motors. Editions Technip, Paris, 1985].
A disadvantage of this scheme in the context of this technical task, is the relatively low frequency of rotation of the output shaft (stator)that does not provide the necessary power characteristics of the engine when drilling bits PDC.
The objective of the proposed invention, representing a downhole hydraulic motor designed for high-speed technology of well drilling with the use of the em type PDC bits, is extending the functionality of PDM through the implementation of the kinematic scheme with additional mobility of the working bodies, providing the possibility of increasing the frequency of rotation of the output shaft PDM, while maintaining the required torque and permissible level of inertial loads.
The task is due to the fact that PDM is made for the two sections of the engine, each section (upper and lower) which includes a screw working bodies on the basis of multiple gyratory mechanism with internal cycloidal gearing, a spindle with an output shaft mounted for axial and radial bearings, hinge connections of the rotor coil of the working bodies with the output shaft and the channels for the passage of fluid, and a stator coil of the working bodies of the upper section still attached to the string of drill pipes, the output shaft of the lower section is connected with the rock cutting tool, and the output shaft upper section by means of rigid links connected the stator coil of the working bodies of the lower section mounted with clearance in the bore of the sub connecting the stationary casing of the spindle sections, and performing concentric rotation in the radial bearings of the connecting sub that allows for additional machining is a possibility of the lower rotor section, located in engagement with the lower stator section and performs a planetary motion, and thereby to realize high-speed mode testing bits.
Principal kinematic feature of the proposed scheme lies in the fact that the angle of rotation of the rotor in a figurative movement insignificantly exceeds the angle of rotation of the rotor in absolute motion, which provides advantages in terms of the action of inertial forces and permissible speed.
For the implementation of mode concentric rotor lower sections around its own axis working volumes screw the working bodies of the upper and lower sections administered in accordance with the kinematic relation of the working bodies of the lower section.
Figure 1 presents a General view of the stated downhole motor, figure 2 shows a cross-section of the working bodies of the sections PDM if the same geometry, figure 3 is a similar cross-section in the case of varying the geometry of the working bodies of the upper and lower sections, figure 4 shows the relative position of the profiles of the rotor and stator of the lower section in one working cycle of the gerotor mechanism with kinematic ratio of 3:4, and figure 5 - position of the profiles of the rotor and stator for special kinematic case when the fixed position of the center of the rotor. For convenience vospire the Oia kinematic profiles of major points in figure 4 and figure 5 marked fixed teeth rotor. Black shaded the current position of the chamber area, varying from zero to maximum value and again decreasing to zero.
Downhole drilling motors with additional mobility is a two-section hydraulic motor, each section of which includes a screw working bodies (2, 3, and 11, 12) on the basis of multiple gyratory mechanism with internal cycloidal gearing (kinematic pair metal rotor - stator with elastic lining"), the spindle with the output shaft (8 and 18)mounted on the axis (7 and 17) and radial (6 and 16) supports, hinge (4 and 14) the connection of the rotor to the output shaft and the channels for the passage of fluid (and, b), with the upper section made by the scheme of the planetary mechanism with a fixed stator), and the lower section on the differential mechanism.
The stator 2 of the upper section still attached to the string of drill pipe 1 and the output shaft 18 of the lower section is connected with the rock cutting tool 19. The output shaft 8 of the upper section by means of rigid links connected to the stator 11 of the lower section, which is housed with clearance in the bore of the sub 10 connecting the stationary casing 5 and 15 of the spindle sections, and mounted in a radial bearing 13 for the purpose of rotational movement of the stator 11. For upl is Tania output shaft 18 of the engine the pressure in the working bodies of the lower section in the bore of the connecting sub 10 can be installed mechanical seal 9 or sealing device of another type.
The device operates as follows (figure 1). When the flow of drilling fluid through the hydraulic fluid passage of the drill pipe 1 in the upper section of the working bodies is made the duty cycle at which the rotor 3 performs a planetary motion, objetivas along the spiral teeth of the fixed stator 2 with eccentricity einequal to the axial distance a screw gyratory mechanism of the upper section. Rotation of the upper rotor 3 through the pivot joint 4 is installed in the 6 radial and axial 7 spindle bearings output shaft 8 of the upper section, which, in turn, drives the stator 11 of the lower section, making concentric rotation within a sub 10 in the radial bearing 13, which provides additional mobility of the working bodies of the lower section leading rock cutting tool 19. During the rotation of the stator 11 mated with him, the rotor 12 of the lower section performs the planetary motion, in which the rotor rotates around its own axis, and the axis is drawn around the axis of the rolling stator 11 in the opposite direction of the eccentricity enscrew gyratory mechanism of the lower section. Rotation of the lower rotor 12 through a swivel 14 is transmitted to the output shaft 18 of the lower section, set 16 in the radial and axial supports 17 of the spindle.
In the output shaft h is sung section, associated with the rock cutting tool such as a drill PDC, rotates with the frequency depending on the ratio of working volume screw top (Vin) and lower (Vn) sections (figure 2), and the flow rate Q of the mud.
To effect the rotation of the rotors of the upper and lower sections in one direction and thereby adding the angular velocity at the output shaft of PDM working bodies of the sections must have the same direction of the helical cuts. The length of the working bodies must comply with the specified torque and is assigned depending on the tolerable inter-turn differential pressure.
In the General case, without regard to volume losses, the frequency of rotation of the output shaft PDM or absolute frequency of rotation of the rotor lower sections
where nin- frequency of rotation of the output shaft upper section, nin=Q/Vin;
nOTN- the relative frequency of rotation of the rotor lower sections, nOTN=Q/Vn.
Thus, the rotational speed of the output shaft PDM can be represented as a function of frequency of rotation of the upper rotor section and the relationship of displacements screw the ar sections:
Kinematic indicator workflow PDM with additional mobility, is the coefficient multiplier equal to the ratio of the frequencies of rotation of the output shaft and the rotor top section:
Taking into account expressions (2) the coefficient multiplier and the ratio of working volume coil pairs are connected by the following dependency:
In the particular case when working bodies of the upper and lower sections have the same working volume (Vn=Vin)what can be achieved by the application of identical coil pairs (figure 3) with the same kinematic ratio, eccentricity and step spiral surfaces, the rotational speed of the output shaft PDM
Thus, when using the same screw in the diagram, the output shaft speed is doubled.
For any kinematic scheme PDM with additional mobility (stator or rotor) the workflow cycle, during which through working bodies with the number of visits of the stator and rotor, respectively, z1and z2passes the volume of liquid equal to the volume of the working chambers is turning the rotor in absolute motion on the corner
where φSS- the angle of rotation due to the additional rotation, φSS=2πnint (t is the time corresponding to the relative rotation angle of 2π/z2).
I.e. the multiplicity of actions PDM with additional mobility, corresponding to the number of cycles per revolution of the output shaft
Characteristics and performance of structural elements of PDM with additional mobility is largely dependent on the ratio of angular velocities of the absolute and portable motion of the rotor.
In the General case, the angle of rotation of the center element (rotor or stator)performing a planetary motion in PDM with additional mobility (respectively the stator or rotor) is defined as follows
where zplan- the number of visits planetary moving element of the working bodies (internal z2or outdoor z1); & Phi;Rel- the rotation center relative movement with respect to concentric rotating element, turning on the angle φSS.
The plus sign refers to the case of planetary moving stator, mn is to minus - to celebrate moving planetary rotor as in the present invention. Here the angle of rotation φSScorresponds to the angle of rotation of the output shaft upper section: & Phi;SS=φin.
the ratio of angular movement of the portable and absolute motion gets
the expression (10) finally takes the following form
For this invention with a planetary moving rotor (inner element of the working bodies) angles of rotation of the rotor in a figurative and absolute motion is treated as
Note that in this case the rotor and the center of the rotor, as in the model scheme PDM with a fixed stator are rotated in opposite directions. Principal kinematic feature of the proposed scheme is that the rotation angle of the rotor is in a figurative movement is always less than z 2times the angle of rotation of the rotor in absolute motion, which distinguishes the scheme in relation to the action of inertial forces and permissible speed compared to another possible scheme with planetary moving stator, and a version of the model PDM.
As an example, consider the kinematics of PDM with additional mobility due to the rotation of the stator, taking the kinematic ratio of 3:4 (z2=3; z1=A) and the coefficient multiplier k=2 (figure 4).
The multiplicity of action of the screw mechanism j=3/2, the workflow of this kinematic scheme is carried out during rotation of the rotor angle φ=Δφ=2π/j=240°, while the stator is rotated by an angle of 120°, and the axis of the rotor in a figurative movement on the angle φlane=-(3-2)∙×240=-240°.
If the condition
According to the classification proposed layout PDM refers to the variant of the kinematic scheme screw screw mechanism of the type B-I, in which extra mobility is due to the rotation of the stator and an output shaft connected with the rotor and stator do rotate with different angular velocities [Balenko J.F. ñ, Balenko FD, Gnoevykh A.N. Single-rotor hydraulic machines, vol.1- M: IDC Gazprom, 2005, p.28].
The technical result and the economic effect of the proposed use of the device is achieved by improving the efficiency of drilling bits PDC due to the possibility of realization of optimal speed limits testing.
1. Downhole drilling motors, consisting of two sections - upper and lower, each of which includes a screw working bodies, made on the basis of multiple gyratory mechanism with internal cycloidal gearing, a spindle with an output shaft mounted for axial and radial bearings, hinge connections of the rotor screw working on the bodies with the output shaft and the channels for the passage of fluid, moreover, the stator coil of the working bodies of the upper section still attached to the string of drill pipes, and the output shaft of the lower section is connected with the rock cutting tool, characterized in that the output shaft of the upper section by means of rigid links connected to the stator coil of the working bodies of the lower section mounted with clearance in the bore of the sub connecting the stationary casing of the spindle sections, and performing concentric rotation in the radial bearing of the connecting sub.
2. Downhole drilling motor according to claim 1, characterized in that the working volume of the screw working bodies of the upper and lower sections administered in accordance with the kinematic relation of the working bodies of the lower section according to
where VinVn- working volume respectively of the upper and lower sections;
z1, z2- the number of visits, respectively, of the stator and rotor bottom section.
SUBSTANCE: drill string bottom part assembly comprises downhole motor fitted at said drill string and having rotor and stator. Note here that first hole is made in said rotor. Spindle arranged under downhole motor with second hole made therein. Third hole is made in the shaft with first and second ends. First end is coupled with rotor via first universal adapter. Second end is coupled with spindle via second universal adapter. Inner rod is fitted in the shaft third hole. Note here that inner rod has inner passage and third and fourth ends. Third end seals communication of inner passage with the rotor first hole while fourth end seals communication of inner passage with the spindle second hole.
EFFECT: transducer signal transmission, power supply inside assembly spinning elements.
21 cl, 8 dwg
FIELD: oil and gas industry.
SUBSTANCE: device contains a hollow body with a gerotor screw mechanism inside that includes a stator placed in the body coaxially and a rotor installed inside the stator and the rotor rotation is carried out by fluid delivered by the pump, a transmission section that includes a shaft mounted at the axial bearing made as a multirow thrust and radial bearing and at the upper and lower radial skid bases consisting of the outer and inner sleeves placed in the transmission section body and respectively at the transmission section shaft; the transmission section shaft is fixed at the input by a drive shaft with a rotor and at the output it is fixed with a chisel; the motor is equipped with the upper collar grab consisting of a shaft, a thrust and a nut and the lower collar grab made as a fishing collar with the outer fishing clamp, a thrust collar and the lower threaded crossover with an inner fishing clamp; the upper collar grab is fixed to the upper part of the gerotor screw mechanism while the lower collar grab in mounted at the transmission section shaft between the inner sleeve of the lower radial bearing and the axial bearing made as a multirow thrust and radial bearing. The transmission section shaft and the fishing collar of the lower collar grab with the outer fishing clamp are fixed rigidly with each other by means of a common thread thus providing tightness at butt ends of the thrust collar placed between butt ends of the fishing collar and the inner collar of the lower radial skid base. Cross-threading direction of the transmission section shaft and the fishing collar of the lower collar grab coincide with the direction of drill string rotation during tripping out.
EFFECT: improving accident-free operation, service life and reliability of motors, accuracy of hole making and the rate of parameters set for the hole curvature and passing ability.
5 cl, 2 dwg
FIELD: oil-and-gas industry.
SUBSTANCE: proposed method comprises measuring the pressure in injection line with loaded and idle bit and maintaining constant measured differential pressure. Note here that maximum tolerable bit feed speed (Vtf) is defined by mathematical formula. Then, bit feed speeds are defined and in case it exceeds said maximum tolerable magnitude it is decreased to Vtf.
EFFECT: higher efficiency of drilling.
SUBSTANCE: invention refers to drilling equipment, and namely to downhole motors for well drilling. A spindle includes a housing, a throttle and a shaft with a through axial channel, which is installed in the housing with possibility of axial movement within the limits of a guaranteed play. Between three sealed radial supports there installed are two sections of a multistage bearing plate to take an axial load in downward and upward directions. Each stage of the bearing plate consists of discs with supply hydraulic channels and flow centre plates, the rubber elements of which have annular chambers forming together with discs the thrust hydrostatic bearings. A throttle is replaceable and installed in an axial channel of the shaft. Diameter of the throttle pass for creation of pressure drop is chosen in compliance with an expected hydraulic load on the axial support in start-up operating mode of the motor. On outer surface of the shaft there are blind longitudinal slots hydraulically connecting in a separate manner a cavity above upper radial support to annular chambers of the upper section of the bearing plate and a cavity above the middle radial support to annular chambers of the lower section of the bearing plate. The cavity above lower radial support is hydraulically interconnected with the shaft axial channel below the throttle.
EFFECT: improvement of a motor structure.
1 cl, 3 dwg, 2 tbl
FIELD: oil and gas industry.
SUBSTANCE: unit to control power load onto working elements of a screw downhole motor comprises a half-coupling with radial and axial through channels, a spring-loaded container installed in the axial through channel of the half-coupling with a hydraulic monitor attachment, a burnisher of alternating cross section, installed as capable of axial displacement, a spring and seals. It also comprises a hollow pressing nut installed in the axial through channel of the half-coupling for interaction with the spring-loaded container and with an inner ledge made in the axial through channel of the half-coupling or the burnisher. The burnisher is made in the form of a replaceable tip installed onto the stem.
EFFECT: makes it possible to increase efficiency, reliability and durability.
3 cl, 1 dwg
FIELD: engines and pumps.
SUBSTANCE: motor includes a housing with a rotor arranged inside it, the rotation of which is performed by the fluid medium supplied with a pump, as well as a spindle housing with a shaft arranged inside it, which is installed on radial and axial sliding supports. The spindle shaft is attached to the motor rotor and a bit. Some amount of fluid medium is pumped through radial and axial sliding supports, and axial support of the spindle is made in the form of two pairs of rotor and stator rings with an annular row of thrust modules, which is fixed in each of them. Stator rings are fixed in the spindle housing, rotor rings are installed on the spindle shaft, and each thrust module includes layers of polycrystalline diamonds on the edge facing the edges of adjacent modules, and contacts in turn with one or two edges of adjacent modules. The motor includes a splined bush with external splines, which is installed on the spindle shaft, and two elastic damping supports arranged on the edges of the splined bush and receiving axial forces acting on the axial support of the spindle. Each elastic damping support contacts the rear edge of the corresponding rotor ring with the fixed annular row of thrust modules, and rotor rings with annular rows of thrust modules fixed in them are provided with internal splines corresponding to external splines of the splined bush, and each of them is installed with possibility of annular distortion of the rotor ring with the annular row of thrust modules, which is fixed in it, relative to its own elastic damping support.
EFFECT: increasing service life and improving reliability of the axial sliding support of the spindle of the hydraulic downhole motor with thrust modules; improving accuracy of curvature parameters of the well shaft; enlarging the hole boring per bit run using hydraulic jars in the tubing; increasing the increase rate of curvature parameters of wells, and reducing stresses in the layout of the bottom of the drill column and downtime of the drilling unit.
6 cl, 5 dwg
FIELD: machine building.
SUBSTANCE: device includes frame 2, powder brake 3, kinematic chain A between outlet shaft of HBM 1 and rotor 4 of powder brake 3, hydraulic baffle plate 5, monitoring and testing unit 6 and date control and processing unit 7. Kinematic chain A is made in the form of gear-type conical multiplier 8 with coupling clutches 9, 10 in connections of its shafts 11 and 12 with outlet shaft B of HBM 1 and rotor 4 of powder brake 3. Hydraulic baffle plate 5 is made on cover plate 13 of multiplier 8 in the form of an annular reservoir enclosing with seal 14 the lower part of housing B of HBM 1.
EFFECT: improving accuracy and enlarging the HBM loading range at testing, and possibility of stand-alone use.
FIELD: machine building.
SUBSTANCE: invention is used for run-in and test of hydraulic bottomhole motor (HBM). When testing HBM 1, it is installed in a vertical position above well 2 of its further operation and attached to housing A by means of spinning wrench 3 on stationary drilling outfit 4 of well 2. Outlet shaft 5 of spindle 6 of HBM 1 is attached through coupling device 7 to inlet shaft 8 of multiplier 9 installed on rotary table 10. Rotation of rotor 11 with spindle 6 is performed by injection of working fluid to HBM 1 through adapter 12 of pump station 13 of drilling outfit 4 of well 2. Mechanical loading of outlet shaft 5 of spindle 6 is performed through multiplier 9 kinematically connected at its outlet shaft 15 to powder brake 17, with further measurement and analysis of revolutions and braking moments at the outlet of the latter, and flow rate and pressure of working fluid at HBM 1 inlet.
EFFECT: improving accuracy of the method and its approximation to HBM operating conditions.
FIELD: machine building.
SUBSTANCE: invention is used for run-in and test of hydraulic bottomhole motor (HBM). Bench includes drive device 2 having pump station 3, pressure line 4 and assembly 5 for attachment of HBM 1, loading device 6 having frame 7 and powder brake 8 kinematically connected to outlet end of HBM 1, monitoring and testing unit 9 and data control and processing unit 10. Loading device 6 is equipped with conical multiplier 11 with hollow inlet shaft 12 located normally to base 13 of frame 7. HBM 1 is installed in cavity 14 of inlet shaft 12 of multiplier 11 with outlet end with chisel 15 conjugated with half-coupling 16 made with cams A for chisel 15 at inlet shaft 12 of multiplier 11, the outlet shaft 17 of which is kinematically connected to rotor 19 of powder brake 8. Loading device 6 is fixed on rotary table 20 coaxially to inlet shaft 12 of multiplier 11. Drive device 2 is made in the form of a stationary drilling rig of well 21.
EFFECT: increase in testing accuracy and approximation of the bench design to HBM real operating conditions.
FIELD: machine building.
SUBSTANCE: screw hydraulic machine includes rotor and stator of screw shape without any elastomeric coating, which are installed with a gap. Stator is solid metal alloy ceramic or composite material. Rotor is directed on its ends with guide system to exclude direct contact to stator. In addition, rotor surface or stator surface have grooves.
EFFECT: improvement of screw machine design is provided.
16 cl, 7 dwg
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.