Turbodrill turbine

FIELD: oil and gas well drilling equipment, particularly axial flow turbine of multistage turbodrill.

SUBSTANCE: turbodrill turbine comprises stator with blade ring and inner rim, rotor with blade ring and hub. Design angles of stator flow inlet and outlet directions α2 and α1 and rotor flow inlet and outlet directions β2 and β1 are related by theoretical correlations with peripheral velocity determined in idle and optimal (shock-free) mode of turbine operation. Stator and rotor blade ring blades defining above design angles as distinct from prior art turbines are formed so that shock-free regime of flow around the stator and the rotor is realized at different peripheral velocities, wherein above shock-free regime of stator flow-around is performed in retardation mode, shock-free regime of rotor flow-around is performed in runaway mode thereof. Above stator and rotor angles are correlated as α12≤π/2 and β21≤π/2 (in the case of positive reactive turbine) and β12≤π/2 (for negative reactive turbine). The stator rim has surface of lesser diameter having conoid shape and converging towards lower cross-section thereof so that minimal annular gap defined by rotor hub is 0.05-0.3, preferably 0.1-0.2 of radial stator blade height and inner blade ring surface of lesser diameter has conoid shape and is converged to upper section so that radial rotor blade height ratio in lower and upper sections is equal to 0.7 - 0.95.

EFFECT: increased axial support resistance along with increased performance.

5 cl, 8 dwg

 

Now the present invention relates to the technical tools designed for drilling oil and gas wells, and in particular, to the execution host structures multistage rotary drills axial turbine.

A known design of axial turbine multi-stage turbo-drill, profile blades which ensures their unstressed wrap (optimum) on the frequency of rotation of the shaft and smaller than on extreme mode (maximum power). Such turbines are called vysokoselektivnymi and distinctive feature is the dependence of the line pressure from the rotation frequency with the increase in its mode of slipping and falling to the brake mode (see "Hydraulic machines and compressors. Kasyanov V.M., M.: Nedra, 1970, p.28-35). Application vysokoselektivnyi turbines in practice (so-called turbine with an inclined line pressure) provided some ability to control the mode of operation of the turbo-drill pressure on the surface and, in addition, with use of special devices, in particular valve has been reset part of the fluid past the turbine, thus limiting the upper frequency of the shaft of the turbo-drill and drill bit. This was achieved by increasing the main parameter of the turbine - relations braking torque for accelerating the rotational speed, i.e. the increase in the slope of the IOM is nteu characteristics.

The main disadvantage vysokoselektivnyi turbines is the fact that a significant rotation of the jet in signosagencia blade apparatus with minimized its axial height (one of the most important design requirements of a multi-stage turbo-drill) is associated with increased energy losses and reduced efficiency compared to normal - and nizkochastotnymi turbines, the optimal mode which respectively coincide with extreme speed and exceeds it. Another important disadvantage vysokoselektivnyi turbines is the difficulty of making their precision casting method, in a greater degree is necessary for such a profile shape of the blades, but is associated with increased complexity, cost, and often the impossibility of its implementation especially at small axial dimensions of the flow channel of the turbine. Moreover, the use of vysokoselektivnyi turbines with valve was discontinued due to low reliability of constructions of valves. At the same time from all widely tested control systems characteristics turbodrills specified method was the most concise, without requiring complex and cumbersome devices, such as system hydrocortone, compounds in the form of a turbine with coil motor and the like (including gear turbodrill).

Know what role in shaping the AI output characteristics of the turbodrill play leakage of drilling fluid in the annular gaps of the turbine (see "Theory and design of multistage axial turbine turbodrills". Goulubkov and Bgolubov. Costoptimized 1963, p.56-64). From the point of view of minimization of leaks, these gaps are trying to reduce, but on the other hand to increase, based on the technological requirements of drilling in contaminated or containing cladding filler solutions (see RF Patent №2174584, CL E 21 In 4/02, 19.12.2000).

The last of these sources is the analogue of the invention. It describes a turbine stage with an increased radial clearance between the rotor blades and the hub of the stator, being in the range from 0.1 to 0.2 from the radial height of the rotor blades of the crown, and, in addition, the angle of the chord of the blades of the stator and rotor to the plane perpendicular to the axis of the turbine, differ by an angle of more than 20° when their respective values not more than 50° and at least 70°.

Arguing that these signs reduce to a minimum hydraulic axial load on the rotor of the mud motor, the authors generally ignore well-known from theory of turbines communication design parameters of the profiles of the blades of axial-flow turbines with the activity coefficients and reactivity, which are determined by the components of the hydraulic load on the stator and the rotor of the turbine from the effective (useful) saboten is in her head. Minimize axial hydraulic load on the rotor is achieved in turbines with the activity coefficient close to 1 (and reactivity - 0). Thus the value of the angle of the chord of the blade is a direct consequence of the chosen values of the degree of activity (reactivity) stage and is determined by calculation using known from theory of equations. However, while not disputing the protected objects, note that in this design the turbine is not achieved the goal of increasing steepness torque characteristics, as even with increased radial clearance between the rotor rim and the stator hub in the mentioned patent, none of the structural features do not allow us to carry out artificial change the torque characteristics of the turbine in the direction of increase of the braking torque for accelerating the speed of rotation.

In this respect it is of interest RF patent №2032063, CL E 21 In 4/00, 09.04.92 taken as a prototype of the invention. Here turbodrill turbine containing a stator and a rotor with profiled blades with different angles of inclination of the blades to the plane perpendicular to the axis of the turbine, with different angles of input and output edges of the rotor and stator, with various forms of working surfaces of the blades of the rotor and stator having outer and inner rims of the stator and various'm glad the real height of the blades of the rotor and stator. Protected in the patent signs sometimes contradictory and vague (for example, edges of the blades may not be inclined to the plane in which they lie, see part 3). But most importantly, in this patent with clearly defined objectives create a turbodrill turbine with the regime of maximum power, controlled by line pressure and increased this parameter is the ratio of torque to speed, not solved and is not described none of the design features that increase the slope of the torque characteristics of the turbodrill. It is argued that achieving a high value of the parameter M/n. However, firstly, not shown, through which this occurs, and secondly, this parameter does not determine the slope of the torque characteristics, having a different value from 0 to accelerating the speed toat broken turbine. The slope of the torque characteristics are determined, strictly speaking, the derivative dM/dn, or, for a linear dependence of M(n) - the ratio of the braking torque to stall speed, i.e. Mt/nx. As follows from the Euler equation for axial turbines (see page 5), equal to the estimated diameters of the turbines, the cost and density of the drilling fluid, this value is constant and does not depend on the type and profile of the blades.

Due to lack of steepness of the torque characteristics of the serial construction is of Uroboros increasingly lag behind the requirements of modern drilling as a roller, and PDC bits for which a lower speed (for the first) and elevated values of moments (second) one way or another connected with the necessity of increasing the value of Mt/nxcomparable to how it is peculiar to modern surround the engine or gearbox to turbodrills, but without the known disadvantages of these machines, namely lack of resistance of the working bodies of the screw engines especially at elevated temperatures or lack of reliability and complexity gear turbodrills.

Technical task, which directed the present the invention is the requirement to create a turbine drive bits for drilling, characterized by the necessary slope of the torque characteristics of a cone and PDC bits with a considerable reduction of the load on the shaft bearing from the pressure drop in the turbine and, in addition, the requirement to provide the necessary quality and affordable cost of the turbine stages of the turbodrill.

The solution of the technical problem is achieved by the fact that turbodrill turbine includes a stator blade with a crown with an inner rim and the rotor blade ring gear and the hub, the blades of the stator and rotor rims have structural angles, measured from the plane perpendicular to the longitudinal axis of the turbine, to the tangent to the rofiles blades at the inlet (α 2- stator and β1- rotor) and the output (α1- stator and β2- rotor) connected by relations:

whenwhere ux- circumferential velocity at the estimated diameter of the turbine at her with idle rotation, cz- the axial velocity of the flow through the blade crown, ubr- peripheral speed of the rotor blades on the calculated diameter, which is shock-free flow, uBST- same for shockless flow blades of the stator, [And] is a valid value in the range (0,5...5,0), and for a given value of ux

0<uBST<ux/2≤ubr<uxand α12<π/2 β21≤π/2, and in formulas (1)to(3) sign (+), and if it β12≤π/2 sign (-) in the same formula, in addition, the surface of the smaller diameter of the inner rim of the stator crown made conoidal form with tapering to the bottom section so that the smallest radial clearance between this surface and the rotor hub is within the range from 0.05 to 0.3, preferably from 0.1 to 0.2 from the radial height of the blades of the stator and the inner surface of the smaller diameter of the rotor is about crown made conoidal shape with a narrowing of the upper section, moreover, the ratio of the radial height of the blades in the lower and upper sections of the rotary crown is placed in the range of 0.7 to 0.95.

The invention consists in that the profiles of the blades of the stator and rotor are such that the modes of their unstressed wrapping unlike virtually all commonly used in turbodrills turbines do not match, i.e. the speed at which the stator and the rotor are in unstressed mode, various (uBST≠ubrand shock-free flow around the blades of the stator takes place at low turbine speed (extreme left), and shock-free flow around the rotor blades in the field of high speed (to the right extreme mode). Into force of the stator vanes and rotor crowns are performed without the above-mentioned disadvantages of blade systems vysokoselektivnyi turbines (severe curvature of the profile), and thus effect a given ratio of peripheral speed shockless flow blades of the stator and rotor to the stator crown share effectively creativesage pressure turbine is much larger than the rotor, and the pressure drop across the stator increases with increasing rotation speed, allowing automatic control of the torque characteristics of the turbine. This is achieved by performing the profiled channel for discharge of a portion of the work is its flow past the blades of the stator in the annular gap between the blade crown of the stator and the hub of the rotor by increasing the differential pressure on the blade crown of the stator in the region of the accelerating momentum and minimize these leaks fluid at the lower pressure drop in the low speed close to the brake mode. Thus, the turbine stage and, therefore, multistage turbodrill develop braking torque corresponding to the calculated (technologically necessary for rinsing wells) liquid flow, and have reduced the accelerating momentum, corresponding substantially smaller flow rate, ie the requirement to increase the slope of the torque characteristics of the turbodrill. In addition, the turbine stage having a high degree of activity including the possibility of its negative-reactive, good for the bearings of the turbo-drill: - modes idling rotation and leaching wells, with a large momentumsi bits, including with PDC bits, - structures with independent suspension shaft sections, and also in the modes low speed when you increase the hydraulic load on the rotor, comparable with the increasing weight on bit (axial bearing).

The invention is illustrated by the figures, in which:

figure 1 is a longitudinal section of part of the turbodrill with the speed turbines,

figure 2 - piece crown stator (fragment),

figure 3 - piece crown rotor positive reactivity (fragment),

figure 4 - blade crown rotor negative is considerable reactivity (fragment),

5 is the ground speed of the turbine positive reactivity,

6 is a polygon speed turbine negative reactivity,

Fig.7. dependence of the pressure in the turbine it speed,

Fig - power turbodrill.

In the case of the turbo-drill 1 (figure 1) posted stators 2 multistage turbine with blade rims 3 and the inner rim 4. On the shaft of the turbo-drill 5 posted rotors 6 hub 7 and the blade 8 crowns. The surface 9 of the rim 4 is made conoidal form with tapering to the bottom section. The inner surface 10 of the crown 8 is made conoidal shape with a narrowing of the upper section. On blade rows 3 stator posted by vanes 11 (2), tangent to the profile to the input (a2) and output (a1) parts of the profile or to the midline (a0) - which at the entrance to the interscapular channel form an angle of α2and output - α1with the plane perpendicular to the axis 0-0 of the turbine. The corners of the blades of the stator are in the ratio α12≤π/2. On the blade rings 8 of the rotor placed vanes 12 (3) or 13 (4), tangent to the profile to the input (b1) and output (b2) parts of the profile or to the middle line (b0) - which at the entrance to the interscapular channel form an angle of β1and at the exit β2with the plane, perpendicu Arnau axis 0-0 of the turbine. The difference between the shoulder blades by type 12 and 13 is that for the first β21≤π/2 (positive reactivity), for the second β12≤π/2 (negative reactivity). The annular channel 14 between the surface of the hub 7 and conoidal surface 9 with the narrowing of the axial length of the lower section is characterized by a value δwiththe minimum radial clearance within the limits 0,05 0,3...from radial height (Lto) stator blades 11, which determines the size of the living section of this channel. Internal khodala surface 10 of the rotor of the crown determines the ratio of the radial height of the blades of the lower and upper sections of the rotary crown in the range 0.7...0.95 to.

The setting values of the angle profiles of the blades of the stator and rotor is made from the following considerations.

Torque of a single-stage axial turbine turbodrill according to the formula of Euler is defined as

M=ρQr(c1u-c2u),

where ρ - the density of the fluid, Q is its volumetric flow rate, r is the average (estimated) radius of the turbine, c1uand c2uprojection of the absolute velocity of fluid flow at the inlet and outlet of the rotor in the direction of its peripheral speed u.

When the turbine is stopped (u=0) braking torque step

Mt=ρQrux,

where uxthe ones surrounding the Naya speed of rotation, defined polygons velocities (figure 5 and 6):

ux=cz(ctgα1±ctgβ2),

where cz- the axial velocity of flow through the vane crowns the turbine, the plus sign (+) corresponds to the positive-jet turbine (figure 5), a (-) sign for negative-jet turbine (6).

From the practice of constructing turbines turbodrills acceptable values for the turbine efficiency (>45%) in the operating modes are achieved if the

where the size range And in range (0,5...5,0).

When the optimal mode of operation of the turbine (peripheral velocity at which the efficiency reaches its maximum) the direction of the flow velocities at the inlet vanes of the stator (absolute speed c2) and rotor (relative velocity w1) coincide with the directions of, the relevant constructive corners of the blades of the stator (α2) and rotor (β1)that determines the mode unstressed wrap. As a rule, for all turbines used in practice, this regime occurs for the stator and rotor at the same peripheral speed optimal mode of the turbine and is ground speeds as

uopt=cz(ctgα1±ctgβ1)=cz(ctgα2±ctgβ2).

If we consider this double equality separately, you can write:

ubr=cz(ctgα1/sub> ±ctgβ1) - peripheral speed mode unstressed wrapping rotor blades

uBST=Cz(ctgα2±ctgβ2) - peripheral speed mode shockless flow blades of the stator.

In the invention constructive angles of the blades of the stator and rotor crowns are chosen so that ubr≠uBST(figure 5 and 6), and the mode shockless flow blades of the stator are displaced in the area of low speed until the brake mode, the rotor, on the contrary, the mode shockless flow is shifted to the area of the accelerating speed of the turbine, i.e. the

0≤uBST<ux/2≤ubr≤ux,

in this constructive angles of the blades of the stator are in the ratio:

α12π/2,

and constructive angles of the rotor blades in proportions:

β21≤π/2 for positive-jet turbines (figure 3),

β12≤π/2 for negative-jet turbines (figure 4).

The turbodrill turbine operation.

The flow of drilling fluid (mud) with a volumetric rate Q given diametral dimensions of the flow part of the turbine determines the axial velocity in the blade rows of stator and rotor cz. Using the above formulas and asked valid values maximum castorena turbodrill shaft (n x) with the corresponding value of the peripheral speed uxthe values of structural angles of the blades of the stator and rotor and the modes of their unstressed wrapping in which the input pressure loss is minimal. As can be seen from the graph (Fig.7), the pressure loss curve (PUst) impact the flow regime of the stator blades (for n> nCST) increase due to increase of the difference (angle) between the angles (α′2that α′′2,...) input flow in blade apparatus of the stator (absolute speed′2with′′2,...) and constructive angle stator vanes (α2). In addition, the magnitude of the pressure drop across the stator varies with change of frequency of rotation of the shaft in accordance with the curve effectively creativesage in stage turbine pressure (Peff), which share attributable to the stator (Rest), is determined by the degree (coefficient) activity of the turbine, which in all modes is significantly higher than the degree (coefficient) its reactivity. This is evident also from the ratio of the projections of average absolute velocity (cmu) and average relative velocity (wmu) in the direction of the peripheral speed. And as for positive-reactive and negative-jet turbines, the higher the absolute value of this ratio, the share srabatyvaet the effective pressure in the stator more. Thus the pressure drop across the stator depending on the shaft speed of the turbine as the sum of its components (PUst+Pest) is incident to the brake mode line Rarticle(n).

At the same time the rotor is opposite to the process of increasing the shock losses (PUDR) approximation to the brake mode due to the increase in the difference (angle) between the angles (β′1that β′′1,...) sign-in blade apparatus of the rotor (relative velocity w′1w′′1,...) and constructive angle (β1), which are summed with rabatyvaemy on the rotor lobes effective pressure (Peff-Rest), forming a line of Pp(n) dependence of the pressure drop across the rotor from the shaft speed of the turbine, increasing to the brake mode.

The pressure drop across the rotor (Rpdetermines the axial load bearing turbo-drill, which, as seen above, is significantly reduced at high speeds (when washing and elaboration of the wellbore), which ensures longer life of bearings of the turbo-drill. In the low speed shaft of the turbo-drill, as a rule, the axial load on the bit is significantly increased, therefore, the resultant of the forces acting on the support from gidravlicheskiy load of the turbine and the load is on the bit, reduced down to zero, which also contributes not only to increase the durability of bearings and to reduce friction losses in the support, freeing up a significant proportion produced by the turbine torque for the efficient operation of the bit.

The total pressure drop across the mud motor (Pt) as the sum of the pressure drops on the rotor and stator do not depend on the frequency of rotation of the shaft, increasing either the idle speed, or remaining almost constant Rt(n)that does not lead to an overload of drilling pumps, promoting normal process of drilling in contrast, for example, from drilling screw engine, in which an increase in the load on bit is accompanied by a significant increase in the pressure of the pumps. This disadvantage is characterized by nizkochastotnye turbine, used for the purpose of unloading the pillars of the turbodrill, excessive increase in the pressure on the riser when braking on the bottom fraught breakthrough diaphragms, or other problems with the drill pump.

At virtually the same as in normal serial turbines, the level of loading of drilling pumps in the new turbine is implemented unattainable for serial turbine as a significant increase in the slope of the torque characteristics. This is achieved through the offset mode shockless flow blades of the stator in the area of low frequencies of rotation and the implementation of the s shaped radial clearance between the rim of the stator and the rotor hub.

During much of the growing dependence of Particle(n) in the annular channel 14 with a certain cross-sectional area occur leakage of drilling fluid (q), sigalda the fluid flow through the blade crown of the stator. For the radial gap between conoidal surface of the rim of the stator and the rotor hub with value δwithwithin the range 0.05...0.3 of the radial height of the stator vanes, provides the functional dependence of the leakage from the shaft speed of the turbine q(n). The magnitude of the leakage in the radial gaps serial turbines, as follows from earlier studies, depending on the size of the radial gap and the pressure difference can be quite substantial and, as a rule, this has a negative impact on power characteristics of the turbine, since it reduces its performance in all modes. In the proposed turbine leakage increases with increasing speed, thus cutting off the right (high-speed) torque characteristics. For example, the calculation for turbine dimensions 195 mm the ratio δ/Lto=(0,1...0,2)indicating the desired change of the leakage in the stator (1.5 to 7.5 l/s flow Q=32 l/s) with increasing turbine speed (from 100...150 to 600...900 rpm). This allows you to provide the output torque characteristic of the turbo-drill shown in the graph (Fig).

It should be borne in mind that passing the blades of the stator portion of the washing fluid (leak) does not receive a spin and does not work in the channels of the rotor, creating only an additional, though small, the pressure loss. To reduce these losses, the inner surface of the crown of the rotor profiled conoidal form, which ensures smooth entry of this part of the flow on the rotor blades. But since the radial clearance in the rotor δpis like the serial turbines, leakage of fluid into the rotor is minimized, and the torque produced by the rotor is determined by actual flow (Q-q) and its corresponding velocity in blade apparatus of the stator. Khodala the shape of the surface 10, providing smooth input leakage stator blade in the apparatus of the rotor also creates the maximum possible radial tightness of his flowing part to increase the estimated diameter of the turbine, which is achieved, in addition to a valid change other Diametric sizes, and also when the ratio of the radial heights of the lower and upper sections of the shoulder of the crown of the rotor in the range of values (0,95 0,7...).

A qualitative description of these processes is illustrated in the example on the chart Fig. Here a series torque characteristics of the turbodrill (lines M1, M2,..., M5) and the corresponding pressure lines (P1, P2,..., P5) glamourbaby the most common diameter 195 mm with the new turbine at a cost of Q from 24 to 32 l/s, but in the absence of leakage of the fluid in the stator. When performing this turbine as previously described (with radial clearance in the stator), the resulting torque characteristics when operating at a constant flow rate of 32 l/s represented by the line M(n) and the corresponding line pressure P(n). If, depending on largesti turbodrills the slope of the torque characteristics in conventional units is the value of Mt/nxfrom 0.5 to 0.65, in the same axial and diametrical dimensions and virtually no increase in design can be increased by more than 30% (up to 0.9), while maintaining the magnitude of the braking torque corresponding to maximum displacement, and the reduction of the accelerating (and working) rotational speed to a value corresponding to the minimum displacement. While ascending to the brake line pressure does not exceed the allowable working pressure at maximum displacement (through P5).

The above-described turbine turbodrill applicable in the construction of the turbodrill for drilling::

modern low-speed roller bits, allowing for reduced frequency of rotation of the working and idle modes to values of respectively 200 and 400 rpm when the working and braking torque corresponding to more vysokooborotnye modes (for example, dimensions 195 mm, respectively 3000 and 6000 N·m), and EIT is aniah pressure pumps, do not exceed the permissible;

- modern bits with almashtirganim weapons (PDC), while at speeds in the range of 250-500 rpm the value of the specific point on the bit of not less than 400 N·m/t,

the work of the turbodrill with a new turbine, characterized by increased resistance to axial supports, unloaded when accelerating and balanced (actually unloaded) working in low-speed mode, while the turbine is characterized by simple geometric forms, without introducing additional complexities in the existing manufacturing technology serial turbines.

1. The turbine of the turbo-drill containing a stator, comprising a blade crown with an inner rim, the rotor including blade crown and the hub, and the blades of the stator and rotor rims have structural angles, measured from the plane perpendicular to the longitudinal axis of the turbine, to the tangent to the profile of the blades at the inlet (α2-stator and β1-rotor) and the output (α1-stator and β2the rotor flux, which are connected by the relations:

ux=cz(ctgα1±ctgβ2); (1)

ubr=cz(ctgα1±ctgβ1); (2)

uBST=cz(ctgα2±ctgβ2); (3)

when

where u x- peripheral speed on the current diameter of the turbine when it is idle;

cz- the axial velocity of the flow through the blade crown;

ubr- peripheral speed of the rotor blades on the calculated diameter, which is unstressed wrap;

uBST- same for shockless flow blades of the stator;

[A] is a valid value in the range (0,5-5,0), characterized in that for a given value of ux

0 ≤ uBST< ux/2, and α12≤π/2;

ux/2 ≤ubr< ux.

2. The turbine of the turbo-drill according to claim 1, characterized in that β21≤π/2, which corresponds to the plus sign (+) in formulas(1)-(3).

3. The turbine of the turbo-drill according to claim 1, characterized in that β12≤π/2, which corresponds to the minus sign (-) in formulas(1)-(3).

4. The turbine of the turbo-drill according to claim 1, characterized in that the surface of the smaller diameter of the inner rim of the stator crown made conoidal form with tapering to the lower section, and the smallest radial clearance between said surface and the corresponding rotor hub is within the range from 0.05 to 0.3, preferably from 0.1 to 0.2 from the radial height of the stator blades of the crown.

5. The turbine of the turbo-drill according to claim 1, characterized in that the internal surface of the smaller diameter rotor crown made conoidal shape with a narrowing of the upper section, moreover, the ratio of the radial height of the blades in the lower and upper sections of the rotary crown is placed in the range of 0.7 to 0.95.



 

Same patents:

FIELD: electromechanical engineering.

SUBSTANCE: proposed generator primarily designed to supply with power borehole instrument of face telemetering system in the course of boring has internal stator and rotor; the latter mounts turbine in its front part that has casing carrying rectangular- or trapezoidal-section helical blades. These blades are free to vary their angle of lift depending on conditions of borehole washing with drilling fluid. Blades may be made of flexible material and have two parts of which one part is joined with turbine casing and other (loose) part is free to bend in transverse plane. In addition, blades may have variable stiffness in cross-sectional area and variable height of cross-section profile; loose parts of blades may be joined with ring. Blade turn limiter responding to maximal discharge of drilling fluid may be provided on the turbine casing.

EFFECT: enhanced operating reliability and extended variation range of drilling fluid discharge through generator turbine.

7 cl, 2 dwg

FIELD: engine manufacturing.

SUBSTANCE: invention relates to method of operation of self-contained power station powered by diesel-generator set. According to proposed method of operation of self-contained power station powered by diesel generator set equipped with additional flywheel and disconnect clutch with automatic control members, additional flywheel is mounted on separate shaft which is connected with diesel-generator set by means of disconnect clutch. Preparatory operation is carried out to set power station into operation with subsequent overcoming of short-time starting resistances from consumer. Additional flywheel is connected to shut down diesel generator set by means of disconnect clutch. Power station is started under no load, and its coming to rated speed is detected by readings of generator shaft speed pickups. Load is connected and intensity of generator shaft speed drop is checked. Information is automatically transmitted to controller wherefrom, at termination of generator speed drop, signal is transmitted to disconnect clutch, and rotating additional flywheel is disconnected from diesel generator set, thus changing the set for accelerated mode of restoration of initial rated speed.

EFFECT: provision of power saving operation at stable conditions for overcoming designed resistance torque and short-time overloads exceeding capabilities of chosen supply source.

1 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.

2 dwg

The invention relates to the field of drilling, in particular, to a downhole motors

Downhole motor // 2224077
The invention relates to downhole motors to drive the rock cutting tool during drilling

The invention relates to a hydraulic downhole motors, which result in rotation of the roller bit, destroying the faces of barrels of drilling wells

The invention relates to the field of drilling, hydraulic actuators placed in the well

The invention relates to the field of drilling, hydraulic actuators placed in the well

The turbodrill // 2195542
The invention relates to a drilling technique for drilling wells in different geological formations, and more specifically to the turbodrill

The invention relates to drilling wells and is used to power Autonomous downhole navigation and geophysical instruments in the drilling process

Geared turbodrill // 2263757

FIELD: oil and gas well drilling equipment, particularly with the use of fluid rotary type drives, namely geared turbodrills.

SUBSTANCE: turbodrill has body, lower coupling sub and upper coupling sub. Single stages of turbines are installed on shaft through keyed connection. Installed on the shaft are ball automatic balancing device, counterweight, axial support, radial support and stop upper and lower nuts. Shaft of turbine section is connected to high speed shaft of reducer gear through tooth-type coupling. Planetary gear is installed on high speed shaft so that planetary gear rotates over fixed wheel and transmits rotation to output shaft through gear wheel. Counterweights are arranged on high speed shaft. Turbodrill is provided with sealing units, membranous lubrication device and high-pressure catheter. Turbodrill also has valves for oil reservoir filling.

EFFECT: increased operational reliability during directional well drilling.

1 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.

5 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: 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: 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.

3 dwg

Boring rig // 2255194

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.

1 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.

4 dwg

Gear mechanism // 2250340

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

Face engine // 2248436

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: 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 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.

2 dwg

Up!