The method of determining the profile of the blades hydraulic turbines turbodrills
(57) Abstract:Usage: in the oil and gas industry, such as hydraulic actuators for rotary drilling. The invention is: to reduce the energy loss of the flow of drilling fluid and increase the efficiency of the turbo-drill due to the exclusion of secondary vortices in the interscapular channel turbine arrays defining the profiles of the blades of the turbine turbodrills, based on the use of a given line of input edges of a given profile in the middle section, the defined width of the lattice, is carried out in this section z and describe parametrically
< / BR>where R(, Z) is the radius of curvature of the profile is the solution of the differential level
where V(z) - input speed; - kinematic viscosity; is the angle of rotation of the thread; 1- the angle of the input stream; x1(z), y1(z) - coordinates of the input flange; x, y, z rectangular coordinate system, the x-axis is directed perpendicular to the front grille, the y axis is along the front lines of the lattice, the z - height of the blade. The invention relates to the oil and gas industry, namely to the hydraulic actuators for rotary drilling, placed in the borehole, and more specifically to the turbodrills.
The turbodrill is a multi-stage hydraulic turbine driven by the flow of drilling fluid from the mud pump. Each stage of the turbine consists of two blade systems: a stationary stator and a rotating rotor.In the stator, the fluid flow is formed to operate in the rotor; fluid flows mainly along the axis of the turbine and around it.Known turbine blades, in which the grating profile height blades designed according to the following laws [1, 2]
the constancy of the axial velocity along the radius WITH1(r) const.the constancy of the exit angle of the fluid flow out of the guide vanes of the stator1n(r) = const.the constancy of the values of Gnrmconst; where Cn- tangential projection of the velocity of the fluid in the blade system; m - factor activity; when m 1 is constant circulation.With all these ways to change the flow direction along the radius in the channels there are so-called secondary flow.Secondary flow in the channel, on the one hand, lead to the redistribution of pressure to improve the tor is rgii flow and reduce the efficiency of the turbo-drill.The cause of secondary currents in channel turbine arrays (applied in practice turbodrills) is that sleek turbulent flow of a viscous fluid lattice is bounded on the ends by walls on which the boundary layers are thicker. Caused by a repeat thread in mesopotam channel centrifugal force to balance which must have increased the pressure on the concave surface of the blade above the pressure on the convex surface of the blade (back), creating a pressure gradient across the interscapular channel. Near the end walls of the flow velocity is reduced, so that the magnitude of the required pressure gradient is reduced. As a result, the pressure on the concave surface of the blade near the walls will be less than the pressure on this surface in the middle section of the blade, which is the reason for occurrence on the concave surface of the blade secondary flow towards the wall. On the convex surface of the blade secondary current is directed from the wall. These currents are superimposed on the main flow in the channel formed by the spiral motion, the so-called vortex pair.The concept of secondary flow entered N. E. Zhukovsky  used HP P is the bot U. R. of Horton  theory of secondary currents in the flow of residual liquid developed, B. Squire and K. G. winter  U. P. Horton 
Secondary energy losses near the ends of the blades in the region of a boundary layer on the walls of the annular channel have been investigated in the work of Howell 
Secondary loss of energy for the turbine lattice with relatively short blades, streamlined viscous fluid comprise half or more of the total losses in the lattice 
Therefore, to improve the efficiency of the mud motor, turbine lattice which has a relatively short blade, the required grating with such design parameters, which significantly reduced the secondary loss of energy.There are many ways of dealing with secondary currents. One of them is running on the end surfaces of the flow part of the gratings across their width special grooves near the back of the blades  Instead of the grooves also make projections and edges  These elements are partially prevent a vortex pair, however, completely eliminate the secondary current, they are not capable. In addition, they themselves are the sources of additional losses.As a prototype the selected method of limiting secondary flows and pressures along the radius. The method is based on the use of inclined blades of the concavity to the axis of the turbomachine  By varying parameters such as the angle of the blades in the circumferential direction, the axial dimension of the crown and twist of the thread is achieved minimum value of the secondary currents.The disadvantage of the prototype is not taking into account the viscous characteristics, environment, and the inability to use this profile inclined blades in lattices of some rotors of turbines, such as high-speed rotary drills.The essence of the invention is to reduce the energy loss of the flow of drilling fluid and increase the efficiency of a turbodrill by eliminating the occurrence of secondary vortices in the interscapular channel turbine arrays.This objective is achieved in that the profile of the blade in the cross-section z is described parametrically
< / BR>where R (alpha, z) the radius of curvature of the profile. Is determined by the solution of the differential equation
< / BR>where V(z) input flow rate;
a rotation angle of the stream;
a1the entrance angle of the stream;
x1(z), y1(z) the coordinates of the input edges;
x, y, z rectangular coordinate system;
the x-axis napina height of the scapula.Known profiles of the blades having a different shape according to the height of the blade. However, in the known constructions, the law of variation of the spin along the radius does not ensure elimination of secondary currents, along with the change in the shape of the profile you want even change the angle of the blades in the circumferential direction, is achieved by moving around the circumference of the individual profiles (cross sections) of the scapula. The use of blades with tangential tilt or saber blades with a large slope in the lattices of impellers some turbomachines are not allowed on condition of providing sufficient strength. Profiling by the proposed method allows to obtain a radially disposed blade, satisfying the condition of absence of secondary currents. Therefore, the proposed method has a new quality. Thus, the proposed method meets the criterion of "novelty."The comparison of the proposed solutions not only prototype, but also with other technical solutions in this area are not allowed to reveal the features distinguishing the claimed solution to the prototype that allows to conclude that the criterion of "inventive step".When determining the surface shape of a thin blade, obte the second viscosity, the following assumptions are made:
1. Each line of flow of the main flow in the interscapular channel is located on a plane parallel to the walls, is a shifted in the direction of the grating pitch line of intersection of this plane with the surface of the scapula.2. The flow velocity at the entrance of the channel has a direction defined by the angle of entry; known longitudinal component of the vorticity and velocity are determined by the distance from the wall.3. Line the front edge of the blade, the width of the grating and the exit angle of the main stream set.To determine the curvature of the profile of the Navier-Stokes equations will receive
< / BR>The curvature, which satisfies equation (1) contains two arbitrary functions A() and B():
< / BR>The radius of curvature is included in the parametric equations profile
< / BR>For example, the solution of the differential equation (1), if the blade in the middle section has a parabolic profile.The condition of parabolicity middle section of the blade is performed when A V2(l), where l polyvista blades.At the same time the profile of the middle section is defined by a parabola
< / BR>where b(l) width of the grid in the middle section.When(Z) ___ 0, f(Z) ___ , C(Z) ___ tg2< / BR>profile according to  degenerates into a straight line , set at an angle2to the stream.In General, the profile of the blade in the middle section can be also approximated by a spline. In the case of solutions of the equation (1) is expressed as a number, which in this description because of the bulkiness and complexity is not given.Sources of information:
1. Suslov PP Turbine drilling. M. Nedra, 1968.2. Kasyanov C. M. Hydraulic machines and compressors. Textbook for high schools, 2nd ed. revised and enlarged additional Meters of the Subsurface. 1981.3. Zhukovsky N. That is About the movement of water at a bend in the river, so IV, lecture notes, 1973, S. 193-233.4. The Prandtl L. Hydromechanics. The SLUDGE. M. 1951.5. Stepanov, Y. Hydrodynamics lattices of turbomachines. Fizmatgiz. 1962.6. Houston U. R. the Application of theory of secondary currents for the challenges of internal aerodynamics, Mechanics, M. 1968, No. 5 (III).7. Squfze H. B. Wfnter R. G. The Secondary flow in a cascade of airfoile in a non-unifrom starea m. J. Alronavt. Soi. 18, 271-277, 1951.8. Hawtorne W. R. Secondary ciraflation in flnud flow. Proc. Rou. Soc. A 206, 374-387, 1951.9. Howell A. R. Flnud dynnamies of axfal-flow compressors. Proc. Inst. Mech. Eng. 153, 441-452, 1945.10. Shvarov Century, To form the blades of the turbomachine, preventing the formation of secondary tx2">12. Tonkov A. M. Tikhomirov A. B. flow Control in thermal turbines. HP Engineering. 1979. The method of determining the profile of the blades hydraulic turbines turbodrills, based on the use of a given line of input edges of a given profile in the middle section, the defined width of the grating, characterized in that the profile of the blade in the cross-section Z is described parametrically
< / BR>where the radius of curvature R1z) profile is the solution of the differential equations
< / BR>where V(z) input speed;
- kinematic viscosity;
- the angle of rotation of the stream;
1- the angle of the input stream;
X1(Z), Y1(Z) the coordinates of the input edges;
X, Y, Z rectangular coordinate system: the X-axis is directed perpendicular to the front grille, the Z-axis along the front lines of the lattice, the Y-axis height of the blade.
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