Screw screw engine with turbine activator

 

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 enables to effectively implement the concept of creating a short downhole motor with a large reserve of torque on its shaft and high life expectancy at relatively low differential pressures on its working bodies. The invention consists in creating multiple coil motor includes: a spindle containing ball heel, radial bearings and labyrinth disk throttle seal and a working section containing a helical screw pair and up to sixty stator and rotor pressure stages of the turbine-activator gyratory pair. Rotary pressure stage of the turbine-activator fixed on the shaft of the working section together with the rotor screw screw pair with the rotary nut and the stator pressure stage of the turbine-activator fixed in the housing of the working section in conjunction with the stator coil gyratory pair with the bottom of the connecting sub. In the case of the working section is placed (fixed) up to 6 steamy stator pressure stages of the turbine and their corresponding hubs rotary pressure stages of the turbine are closed radial end plate rubber seals. The gaps between the ends of the blades of each rotor pressure stage of the turbine and the corresponding stator hub pressure stages of the turbine are closed radius rounding or confused by compressing each located above the stator pressure stage of the turbine from the maximum wetted perimeter. The chord of the stator blades is located at an angle of between 35 to 55oto the plane perpendicular to its longitudinal axis, at the same time, the chord of the blades of the rotary pressure turbine has a tilt angle of from 60 to 90oto the plane perpendicular to their longitudinal axis, and the preferred direction of the slope of the chord of the profile - right screw. 4 C.p. f-crystals, 6 ill.

The present invention relates to means used for drilling oil and gas wells,and in the more narrow their unit to the hydraulic downhole motors, which result in rotation of the roller bit, destroying the faces of barrels of drilling wells.

Distant analogue of the invention is a turboprop engine, described in detail on pages 47...49 source: "Screw downhole motors" - a reference guide, the authors D. F., Balenko, F. D. Balenko, A. N. Gnoevykh, M x it uncompetitive compared to conventional multiple-screw gyratory motor when drilling deviated wells.

Its main drawback is too large axial dimension (typically, from 19.5 to 26 m). When such axial dimension of the engine, the measuring point of curvature and azimuthal direction of the barrel of drilling inclined wells distant from the surface of the deepening of the pit at a distance of 20 to 40 m

Such a large "unaccountable" distance deprive drillers possible to accurately position the spatial position of the BHA in the array of rock.

Because of this, almost 40% of all directional wells in our country do not fall into the circular target, the diameter of which is generally greater than 50 m in order to raise the accuracy of the drill navigation, the engine should be, perhaps shorter.

The closest analogue of the invention is downhole Hydraulic motor" by A. S. USSR 1.601.307, CL E 21 In 4/02, 1990; BI 39 from 23.10.90,

In this author's testimony described downhole hydraulic motor consisting of two motor groups working bodies of different speed (i.e. screw gyratory working pair - low-speed element of design, and turbine - high-speed design element).

And gyratory working pair is mounted in the m mounted rotary pressure stage of the turbine by means of special connecting node auxiliary shaft torsion. This engine also requires an increase in its axial dimensions.

To obtain acceptable values of the torques, the length of such engines may not be less than 20-25 m, which contradicts the requirements of directional drilling. Excessively high pressure drops in turbines with low efficiency, operating at speeds of 100-200 rpm, make it impossible to use giant roller bits with differential pressure at nozzle nozzle more than 3 MPa (instead of the required 7-10 MPa).

Therefore, in the foreign practice of drilling from the use of such engines refused.

The invention enables to effectively implement the concept of creating a short downhole motor with a large reserve of torque on its shaft and high life expectancy at relatively low differential pressures on its working bodies.

The invention consists in creating multiple coil motor includes: a spindle containing ball heel, radial bearings and labyrinth disk throttle seal and a working section containing a helical screw pair and up to sixty stator and rotor speed pressure tny on the shaft of the working section together with the rotor screw screw pair with the rotary nut, and stator pressure stage of the turbine-activator fixed in the housing of the working section in conjunction with the stator coil gyratory pair with the bottom of the connecting sub.

In the case of the working section is placed (fixed) from 4 to 6 stator absorbers-limiting transverse vibrations of the shaft of the working section.

The gaps between the blade rims stator pressure stages of the turbine and their corresponding hubs rotary pressure stages of the turbine are closed radial end plate rubber seals.

The gaps between the ends of the blades of each rotor pressure stage of the turbine and the corresponding stator hub pressure stages of the turbine are closed radius rounding or confused by compressing each located above the stator pressure stage of the turbine from the maximum wetted perimeter.

The chord of the stator blades is located at an angle of between 35 to 55oto the plane perpendicular to its longitudinal axis, at the same time, the chord of the blades of the rotary pressure turbine has a tilt angle of from 60 to 90oto the plane perpendicular to their longitudinal axis, and predpochte screw gyratory motor with turbine activator.

In Fig.2 shows the connection of the lower part of the working section with the screw spindle gyratory motor with turbine activator.

In Fig.3 shows the lower part of the screw spindle gyratory motor with turbine activator.

In Fig. 4 shows the stator and rotor pressure stage of the turbine-activator.

In Fig.5 shows otatara stage pressure turbine-activator.

In Fig.6 depicts a rotary stage pressure turbine-activator.

Using the upper connecting sub 1 case 2 of the working section of the engine is attached to the string of drill pipes. Using the bottom connector sub 3 in the housing 2 due to the axial compression force of still fixated: upper stator adjustment ring 4; rubber screw stator 5 gyratory working couples; stator pressure turbine 6; 4-6 stator damper end 7 of the transverse oscillation of the shaft 8; the lower stator adjusting ring 9.

On the shaft 8 of the working section of the engine through a rotary nut 10 due to axial force compression fixed: rotary spacer sleeve 11; screw rotor 12 gyratory working pair; a rotary pressure stage turbine 13; rotary sleeve is erotinae working couples with the calculated eccentricity that is,

Unlike screw-pairs multiple gyratory motors, for which the elevation angle of the helical line is selected within the range from 60 to 75owith respect to the plane perpendicular to the axis of the rotor (on the basis of the need to ensure self-starting of the engine), the elevation angle of the helical line of the rotor 12 and the stator 5 is selected within the range from 30 to 60o.

That is, the working pair is designed deliberately desmoteplase, which allows for one linear meter of its working body to place multiples of the larger number of steps.

Stator dampers carriage 7 on its inner surface are thick and soft rubber lining 16. The upper rotary sleeve 14 stator shock absorber-limiter 7 is inserted into it with a diametral clearance equal to 2E. The following (in order from top to bottom) of the rotary sleeve 14 is inserted into the corresponding stator dampers carriage 7 with increasingly diminishing gap. That is, the outer diameter of the bushing 14 is increased in order from the upper to the last.

The last one or two sleeves 14 are inserted into the corresponding stator dampers carriage 7 with guaranteed clearance from -15 stator pressure turbine 6.

Each stator stage pressure turbine 6 is mounted relative to the rotary pressure stage 13 so as to ensure the desired distribution of the radial clearance between the blade rim 17 of stator pressure stage 6 and the rotor hub 18 of the rotary pressure stage 13, which may be achieved by using stator absorbers-limiters 7 and the rotary bushing 14.

With the support of the upper rotary sleeve 14 on the corresponding stator damper limiter 7 guaranteed minimum clearancebetween the shoulder of the rim 17 of the upper stator pressure turbine 6 and the rotor hub 18 of the upper rotary pressure stage turbine 13 is 1 mm; the maximum guaranteed clearanceequal 2nd.

Accordingly, the guaranteed minimum clearancebetween the ends of the blades of the upper rotor pressure stage 13 and the corresponding wheel hub 20 of the stator pressure stage 6 is 1 mm; max - 2E. When installed in the working section of the engine 40...60 pressure stages of the turbine with an increasing outer diameter of the rotor bushing 14 guaranteed maximum clearance in the turbine sequence the Torah turbine 6 are positioned relative to each other almost coaxial.

In each stator stage pressure turbine 6, the gap between the blade rim 17 and the rotor hub 16 is closed using radial face plate rubber seal 21, based on the wide upper end of the shoulder of the rim 17. The gap between the ends 19 of the blades of each rotor pressure stage turbine 13 and the hub 20 of the stator pressure stage turbine 13 is closed hydraulic gate, which is formed radius rounding 22, or confused by the compression of the stator pressure turbine 6 by the maximum wetted perimeter, and the respective spatial position of the turbine blades.

The blades 23 of each stator stage pressure turbine 6 are the chord of the profile 24, which is located at an acute anglefrom 35 to 55oto the plane perpendicular to its longitudinal axis. The direction of the chord 24 - right screw.

The blades 25 of the rotary pressure stage turbine 13 are the chord of the profile 26, which is located at an angleto the plane perpendicular to its longitudinal axis.

The value of the anglefits in the range from 90 to 60o.

the possible values of efficiency at speeds from 90 to 150 rpm, preferably the direction of the right propeller.

Such a performance pressure stages 6 and 13 of the turbine-activator allows you to generate on the shaft 8 of the necessary torque to unseat and running Sanatornaya (at rest) screw screw pair (positions 5 and 12).

On the lower threaded end of the shaft 8 is mounted a coupling 27, which rests on the nut-coupling half 28 of the hollow shaft 29 of the spindle motor. In the coupling 28 has a window 30, which is hydraulically report internal boring a cavity of the shaft 29 with the space inside the housing 2 of the working section of the engine that hosts the screw stator 5 gyratory pair and stator pressure turbine 6.

On the shaft 29 by a nut-coupling 28 at the expense of axial force compression fixed: two to four rotary sleeve 31 of stator elements 32 radial bearings mounted in the housing 33 of the spindle; a rotary disks 34 and spacer rings 35 labyrinth throttle shaft seal 29 spindle, a rotary cage 36 ball feet and their spacer spacer ring 37.

In the housing 33 of the spindle motor by means of a connecting sub 38 and valve 39 due to the axial force of the compression fixed: stator elements 32 two to four radial bearings; obretenova heel and spacer spacer ring 43.

The SCREW GYRATORY MOTOR WITH TURBINE ACTIVATOR rotary table of the drilling rig to the lower threaded end of the shaft 29 of the spindle motor is attached drill bit; the upper connecting sub 1 working section is fastened to the first lower candle drill string and begins the descent composition in a wellbore drilled wells.

With increasing depth due to the increasing number of drill candles drill string through the nozzles of the drill bit,the inner cavity of the shaft 29, through the window 30 of the coupling 28 through pressure stage 13 and 6 of the turbine, through the associated line contact gyratory screw (stator 5 and the rotor 12) is filled with mud. About 10 m above the "old" bottom run of the tool is stopped, wrapped around a "head" of the drill string with a leading pipe, square and run in the work of the mud pumps.

Mud is forced through line contact seal screw screw pair and through pressure stage of the turbine, through the window 30 of the coupling 28 in the inner cavity of the shaft 29 and then through the nozzles of the bit in the annular space of the well.

When this dirty solution, saturated sand and mud caught in the drill pipe from the barrel of the camera screw gyratory pairs (items 5 and 12). Sand and mud deposited in milinovich chambers of the gerotor pair in combination with a relatively low elevation angle of the helical protrusions and depressions, eating and inhibit the screw rotor 12 in the stator 5. In order gyratory pair cleared of sand and slurry and rinsed with clean solution, supplied drilling pumps from the surface (i.e. the solution that passed shakers, hydrocyclone battery and a centrifuge), to turn and wind the rotor 12.

This function is performed by pressure stage 6 and 13 of the turbine-activator engine, which due to its structural characteristics are not clogged and not chlemoutsi dirty solution.

When the displacement solution turbine-activator consumes relatively small differential pressure (2 MPa).

After turbine-activator will spin the rotor 12 gyratory pair, her camera cleaned from sand and mud; the friction coefficient drops sharply, and when injected into the engine clean solution gyratory pair starts to work normally, generating the main part of the torque on the shaft 29 of the spindle. After 15-20 min since the launch of the mud pump engine with a chisel is brought to the slaughter; the bit is loaded with an axial load and starts the normal process b is avataram, includes spindle, containing ball heel, the working section, containing a screw gyratory pair of stator and rotor pressure stage of the turbine, characterized in that it contains up to sixty stator and rotor pressure stages of the turbine-activator, with a rotary pressure stage of the turbine-activator fixed on the shaft of the working section together with the rotor screw screw pair with the rotary nut and the stator pressure stage of the turbine-activator fixed in the housing of the working section in conjunction with the stator coil gyratory pair using the bottom connector sub working section, in the case of the working section is up to six stator absorbers-limiting transverse vibrations of the shaft of the working section and the spindle includes a radial bearing of the hollow shaft and has a disk labyrinth throttle seal.

2. Screw screw engine with turbine activator under item 1, characterized in that the gaps between the blade rims stator pressure stages of the turbine-activator, and their corresponding hubs rotary pressure stages of the turbine-activator closed radial end casinomillionaire between the ends of the blades of each rotor pressure stage of the turbine-activator and the corresponding stator hub pressure stages of the turbine-activator closed rounded fillet or confused by the compression of each stator pressure from its largest wetted perimeter.

4. Screw screw engine with turbine activator under item 1, characterized in that the blades of each stator pressure stage of the turbine-activator have a chord that is positioned at an angle of between 35 to 55oto the plane perpendicular to its longitudinal axis, the direction of the chord - right screw.

5. Screw screw engine with turbine activator under item 1, characterized in that the blades of each rotor pressure stage of the turbine-activator have a chord, which is located at an angle from 60 to 90oto the plane perpendicular to its longitudinal axis, the direction of the chord - right screw.

 

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