Gyratory hydraulic motor

 

The invention relates to gyratory hydraulic motors and pumps including multi-stage screw mechanisms, in particular to devices for drilling directional wells. The engine includes a hollow body placed inside multiple multi gyratory mechanism, each stage of which includes a coaxially located stator with internal helical teeth, made of elastic material and mounted inside the stator, the rotor with external helical teeth, number of teeth of the rotor is one less than the number of teeth of the stator, moves the helical lines of the stator and rotor proportional to their numbers of teeth and the axis of the rotor offset from the axis of the stator on the value of eccentricity equal to half the radial height of the teeth. At least two notches of the stator contact in engagement with one rotor or appropriate to these stages of the stator number of stages of the rotor. Speed rotor mounted on a common torsion shaft. The profiles of the teeth of the rotor or the rotor speed in cross section along helical lines at the intersection of the helical teeth of the stator defined by arcs of circles and form the rotor or between adjacent stages of the rotor damper cavity. RSET energy characteristics, resource and reliability of the gerotor mechanism. 7 C.p. f-crystals, 6 ill.

The invention relates to gyratory hydraulic actuators, including multiple multi-screw mechanisms, in particular to devices for drilling directional wells.

Known gyratory mechanism downhole hydraulic machines containing a stator with an internal helical teeth, made of elastic material, a rotor with external helical teeth, which number is one less than the number of teeth of the stator, and moves the helical lines of the stator and rotor proportional to their numbers of teeth, the axis of the rotor is offset from the axis of the stator on the value of eccentricity equal to half the radial height of the teeth, the profile of the teeth of the stator in end cross-sectional envelope as the source of the cycloidal path of Reiki, defined equidistantly shortened cycloid with the equidistant radiusC1[1].

In the known construction the profile of the teeth of the rotor end cross-sectional envelope as another source of a cycloidal path of Reiki, defined equidistantly shortened cycloid, and the equidistant radius RC2Reiki rotor is made larger radius equivalent and the high cost of long monoblock rotors and stators in the performance of their working bodies of the multi-stage and multi-stage (with numbers of more than 4 steps).

Known gerotor hydraulic motor, helical stator which is composed of individual elements, placed in the General case [2]. In the known construction to ensure coincidence of the screw surfaces of each element of the stator is provided with locking elements, pins, protrusions, grooves, and other Drawback of this design multistage engine is the high cost and complexity of elements of the stator, the necessity of their angular orientation during Assembly.

Closest to the claimed is a multi-coil motor, comprising a screw stator containing its axial length, centered on the outer cylindrical surfaces in the motor housing and fixed in the axial direction on its end thrust surfaces between the two resistant ledges in the housing, at least one of which is a thrust end surface of the sub connected to the threaded housing, eccentrically located relative to the stator and being with him in engagement of the helical teeth of the rotor, coupled kinematic device located below the shaft of the spindle [3].

In the known construction the end thrust poverhnosti self-elements of the stator in the circumferential direction relative to the rotor and the possibility of perception of the reactive torque due to their compression between resistant ledges in the housing, which also made in the form of surfaces of revolution, with respect to the diametrical dimensions of the contacting surfaces of the stator and the housing is within 0,96 1,00...and the ratio of the length of the stator element to step its screw thread is in the range 0.4...4,5. The rotor is made of bonded together its elements arranged on the same axis arbitrarily relative to each other in circumferential and axial directions, and any element of the stator is engaged with only one element of the rotor. Kinematic device is attached to the rotor at the junction of its elements.

A disadvantage of the known designs are technological difficulties and the high cost of long monoblock rotor when performing his multi (with more than 4 steps). Another disadvantage of the known constructions are large inter-turn loss of pressure in the annular cavity between the rotor coupling of the rotors by means of a threaded subs, as well as greater length of the gerotor motor. It is not possible to minimize the volume of pressure loss in the gyratory mechanism to reduce the length of the BHA and to increase the intensity change of the Zenith angle at proudcanadian the claimed invention, is to improve energy performance, resource and reliability of the gyratory mechanism of the engine by minimizing the volume and turn-to-turn pressure loss and reduce perekachivayuschih moments rotors, redistribution of tightness of the teeth of the rotor in the stator through the annular damper cavity between the rotors. Another technical challenge is the reduction in the value of multiple and multi-stage engines and improving the accuracy of drilling wells by reducing the length of the engine.

The essence of the technical solutions is that in a gerotor hydraulic motor, containing a hollow body placed inside multiple multi gyratory mechanism, each stage of which includes a coaxially located stator with internal helical teeth, made of elastic material and mounted inside the stator, the rotor with external helical teeth, number of teeth of the rotor is one less than the number of teeth of the stator, moves the helical lines of the stator and rotor proportional to their numbers of teeth and the axis of the rotor offset from the axis of the stator on the value of eccentricity equal to half the radial height of the teeth, according to the invention, at least on the scrap-speed rotor, and speed rotor mounted on a common torsion shaft, and the profiles of the rotor teeth in cross section along helical lines at the intersection of the helical teeth of the stator defined by arcs of circles and form the rotor or between adjacent stages of the rotor damper cavity, and the distance between the ends of the rotor teeth in the damper cavity does not exceed the radial height of the teeth.

The ratio of maximum volume screw chambers between the teeth of the gerotor mechanism, forming an area of high pressure and torque from hydraulic forces in each stage of the rotor, placed in the appropriate stage stator to the volume located downstream of the damper chamber is equal to (0,8...1,2)ewhere e is the eccentricity of the gearing of the rotor relative to the stator.

Each of the damper cavities in the rotor or between adjacent speed of the rotor is closed in the circumferential direction.

Each of the damper cavities in the rotor or between a pair of adjacent stages of the rotor is made in the form of precombustion chambers, located on a circle, and the number of precombustion chambers between the teeth is proportional to the divider, which divides the number of teeth of the rotor or stator.

The ends of the teeth of adjacent stages of the rotor damper is RA relative to the stator.

The distance between the damper cavities gyratory mechanism or the distance from the entrance and exit gyratory mechanism to the nearest damper cavity is at least 1.05 stroke length of the spiral line speed of the rotor.

The damper cavity in the rotor or between adjacent rotor speed is limited in the radial direction, the diameter of the cavities in their teeth.

The torsion shaft and rotors all or part of the steps of the rotor are interconnected devices to transmit torque mainly teeth or slots.

Performing at least two steps stator contact in engagement with one rotor or appropriate to these stages of the stator number of rotor speed and the rotor speed is set for the total torsion shaft, while the profiles of the teeth of the rotor or the rotor speed in cross section along helical lines at the intersection of the helical teeth of the stator is defined by arcs of circles and forming the rotor or between adjacent stages of the rotor damper cavity, and the distance between the ends of the rotor teeth in the damper cavity is not greater than the radial height of the teeth, increases the energy characteristics of the gerotor hydraulic motor.

With respect to max the moment from hydraulic forces in each stage stator, to the volume located downstream of the damper cavity, equal to (0,8...1,2)ewhere e is the eccentricity of the gearing of the rotor relative to the stator, provided the minimum turn-to-turn pressure loss on the lengths of the rotors that are multiples of at least 1.05 stroke length of the screw speed of the rotor decreases the length of the gyratory motor and increase its torque characteristics.

This is due to the reduction of the pressure difference, i.e. the difference per one turn of the screw mechanism, and the specific pressure in the working chambers between the teeth of each stage of the rotor speed stator and redistribution of the tightness of the teeth of the rotor in the stator through a damper chamber between the rotor speed. Redistribution of tightness in the gyratory mechanism appears when changes interturn specific pressure, which reduces the wear resistance of the gyratory mechanism by reducing perekachivayuschih moments, reduce netsentralnoe rotor or rotor speed, mounted on a common torsion shaft.

As a consequence, increases the smoothness, reduced vibration of rotors stators and dynamic loads in the bearings of the spindle.

The execution of the damper cavity in radadiya for one turn of the screw mechanism in the working chambers of each stage of the rotor, having odd or consisting of primes number of teeth. This is due to the synchronization of the working chambers of the high pressure changes interturn specific pressure. Because of this additionally increases torque and efficiency gerotor mechanism, improves smoothness and reduces the dynamic loads in the bearings of the spindle.

The execution of the damper cavity in the rotor or between a pair of adjacent rotors in the form of precombustion chambers, located on a circle, and the number of these precombustion chambers is proportional to the divider, which divides the number of teeth of the rotor and / or stator, reduces the pressure drop per stage gerotor mechanism, in which even or consisting of Prime numbers, the number of teeth is the stage of the rotor. As a consequence, also increases torque and efficiency gerotor mechanism.

During execution of the butt-ends of the teeth of adjacent rotor speed in the damper cavity is displaced in the circumferential direction by an amount not exceeding the amount of eccentricity of the gear stages of the rotor relative to the speed of the stator, with the distance between adjacent damper cavities gyratory mechanism or from the input and output gerotor mechanism to the nearest polostami between adjacent rotors, limited in the radial direction, the diameter of the cavities in their teeth, is further reduced turn-to-turn pressure loss in the degrees of the stator due to the alignment unit pressure in the working chambers of the high pressure forming stage hydraulic forces in each stage of the rotor. It is also due to the reduction of netsentralnoe-speed rotors due to their pulse centering.

When performing at least part of the speed of the rotor mounted on a common torsion shaft, and the torsion shaft and rotors all or part of the steps of the rotor - connected devices to transmit torque, mainly teeth or slots, increases the reliability of the gyratory mechanism during drilling predominantly mud-pulse method of solid rock.

In Fig.1 shows a longitudinal section of a gerotor hydraulic motor, in which two of the three stages of stator contact in engagement with one rotor.

In Fig.2 shows the element I in Fig.1 ring damper cavity.

In Fig.3 shows a section a-a in Fig.1 across the gerotor motor.

In Fig.4 shows a longitudinal section of a gerotor motor, in which three stages of stator contact in engagement with the circumferential direction of the damper cavity gyratory motor.

In Fig.6 shows a cut-across the damper cavity in the form of precombustion chambers located around the circumference of the rotor of the gerotor motor.

Gyratory hydraulic motor includes a hollow body 1 placed inside multiple multi gyratory mechanism 2, each stage 3, 4, 5 which includes coaxially located stator 6 with internal helical teeth 7, made of elastic material and mounted inside the stator, the rotor 8 with external helical teeth 9 (see Fig.1).

Number of teeth 9 of the rotor 8 is one less than the number of teeth 7 of the stator 6, moves the helical lines of the stator 6 and rotor 8 is proportional to their numbers of teeth, respectively, 7, 9, and the axis 10 of the rotor 8 is displaced relative to the axis 11 of the stator 6 on the magnitude of the eccentricity 12(e), equal to half the radial height of 13 teeth 7, 9 (see Fig.1, 3).

At least two stages 3, 4 of the stator 6 are in contact in engagement with one rotor 8 (see Fig.1) or to comply with these steps 3, 4, 5 of the stator 6 number of stages 14, 15, 16 of the rotor, and steps 14, 15, 16 of the rotor mounted on a common torsion shaft 17 (see Fig.4). In addition, in Fig.1 shows a shaft 18 on which is set the stage 16 of the rotor and sealed with the whole rotor 8.

The profiles of the teeth of the rotor 8 or stui 21 circles, the convex face 22 which is turned to the junction 19, 20 of the screw teeth 7 of the stator 6 and formed in the rotor 8 or between adjacent stages of the rotor 14 and 15, and 15 and 16, the cavity 23, 24 (see Fig.1, 2).

The distance T between the ends of the teeth 9 of the rotor 8 in the cavity 23 (see Fig.2) (along helical lines), and between the ends of the teeth 9 of the rotor 8 and the speed of the rotor 16 in the cavity 24 (see Fig.1), between the ends of the teeth 9 of the speed of the rotor 14 and 15 in the cavity 23, and also between the ends of the teeth 9 of the speed of the rotor 15 and 16 in the cavity 24 (see Fig.4), does not exceed the radial height of 13 teeth 7, 9.

The damper cavity 23, 24 in the rotor 8 or between each pair of adjacent stages 14 and 15, and 15 and 16, made in the form of precombustion chambers f, located on a circle, and the number of precombustion chambers between the teeth 9 in proportion to the divider, which divides the number of teeth 9 of the rotor 8 or teeth 7 of the stator 6 (see Fig.1, 6).

The ratio of maximum volume screw chambers 25 between the teeth 7, 9, forming an area of high pressure and torque from hydraulic forces in each stage 14, 15, 16 of the rotor placed in the appropriate steps 3, 4, 5 of the stator 6 to the volume located downstream of the damper cavity 23, 24 is equal to (0,8...1,2)ewhere e is the eccentricity of the gear 12 of the rotor 8, 16, 14 and 15 relative activities is received in the circumferential direction by an amount not exceeding the value of eccentricity 12 (e) gearing levels 8, 16, and 14 and 15, 15 and 16 of the rotor relative to steps 3, 4, 5 stator (not shown).

Sections 3, 4, 5 between the adjacent damper cavities 23, 24 gyratory mechanism or the distance from the inlet 26 and outlet 27 gyratory mechanism to the nearest damper cavity 23 or 24 is at least 1.05 stroke length of the spiral lines of the steps 14, 15, 16 of the rotor (see Fig.1).

The damper cavity 23 in the rotor 8 or between adjacent stages 14 and 15, and 15 and 16 of the rotor is limited in radial direction by the diameter of the depressions 28 of their teeth 9 (see Fig.2).

Torsion bars 17, 18 and rotors all 14, 15, 16, or part of the steps 8, 16 of the rotor are interconnected devices to transmit torque, mainly teeth or splines (see Fig.1, 4), and the splines or teeth are not shown.

In addition, in Fig.1 shows: POS. 29 - spindle section; POS. 30 - bent sub; POS. 31 is threaded casing; POS. 32 is a drive shaft; POS. 33 - threaded sleeve for connecting the bit; POS. 34 - the direction of flow of washing fluid; POS. 35 adapter for drill pipes.

Gyratory hydraulic engine works as follows: the flow 34 of washing fluid under pressure from 40 to 60 kgf/cm

Emerging on the rotors 8, 16, or on the steps 14, 15, 16 rotor torque causes the planetary rotation within stages 3, 4, 5 of the stator 6, which by means of the drive shaft 32 is converted into rotation of the spindle within the spindle section 29 and a threaded sleeve 33 with a chisel. The direction of rotation of the sleeve 33 of the bit opposite the planetary running-in of the rotors 8 and 16 or 14, 15, 16 in steps 3, 4, 5 of the stator 6 (see Fig.3).

Screw chamber 25 have a variable volume and periodically move around the stream 34 of washing fluid, interacting with the damper cavities 23, 24. When the ratio of maximum volume screw chambers 25 between the teeth 7, 9 gyratory mechanism 2, forming an area of high pressure and torque from hydraulic forces in stage 3 of the stator, to the volume below the thread 34 of the damper cavity 23, as well as the amount of stage 4, respectively, to the volume of the damper cavity 24, is equal to (0,8...1,2)ewhere e is the eccentricity of the gear 12 of the rotor 8, 14, 15 and 16 relative to the stator 6, provided the minimum turn-to-turn pressure loss in lengths that are multiples of at least 1.05 stroke length of the spiral steps 3, 4, 5 R the Oia.

The invention improves torque characteristics, efficiency, reliability and gyratory mechanism by minimizing the volume and turn-to-turn pressure losses in the damper cavity and screw the camera, reduces the length of the gyratory motor.

Sources of information

1. RU, patent 2166603, MKI E 21 In 4/02, 2000.

2. US patent 3912426, MKI F 01 C 5/04, 1975.

3. RU, patent 2075589, MKI E 21 In 4/02, F 01 C 5/04, 1994.

Claims

1. Gyratory hydraulic motor, containing a hollow body placed inside multiple multi gyratory mechanism, each stage of which includes a coaxially located stator with internal helical teeth, made of elastic material and mounted inside the stator, the rotor with external helical teeth, number of teeth of the rotor is one less than the number of teeth of the stator, moves the helical lines of the stator and rotor proportional to their numbers of teeth and the axis of the rotor offset from the axis of the stator on the value of eccentricity equal to half the radial height of the teeth, characterized in that at least two stages of stator contact in engagement with one rotor or appropriate to these stages of the stator number of steps RK spiral lines between the teeth of the stator defined by arcs of circles and form the rotor or between adjacent stages of the rotor damper cavity, and the distance between the ends of the rotor teeth in the damper cavity does not exceed the radial height of the teeth.

2. Gyratory hydraulic motor under item 1, characterized in that the ratio of maximum volume screw chambers between the teeth of the gerotor mechanism, forming an area of high pressure and torque from hydraulic forces in each stage of the rotor, placed in the appropriate stage stator to the volume located downstream of the damper cavity is (0,8...1,2)ewhere e is the eccentricity of the gearing of the rotor relative to the stator.

3. Gyratory hydraulic motor under item 1, characterized in that each of the damper cavities in the rotor or between adjacent speed of the rotor is closed in the circumferential direction.

4. Gyratory hydraulic motor under item 1, characterized in that each of the damper cavities in the rotor or between a pair of adjacent stages of the rotor is made in the form of precombustion chambers, located on a circle, and the number of precombustion chambers between the teeth is proportional to the divider, which divides the number of teeth of the rotor or stator.

5. Gyratory hydraulic motor under item 1, characterized in that the end faces of adjacent teeth of the speed of the rotor dampfe the rotor relative to the stator.

6. Gyratory hydraulic motor under item 1, characterized in that the distance between the damper cavities gyratory mechanism or the distance from the entrance and exit gyratory mechanism to the nearest damper cavity is at least 1.05 stroke length of the spiral line speed of the rotor.

7. Gyratory hydraulic motor under item 1, characterized in that the damping of the cavity in the rotor or between adjacent rotor speed is limited in the radial direction, the diameter of the cavities in their teeth.

8. Gyratory hydraulic motor under item 1, characterized in that the torsion shaft and rotors all or part of the steps of the rotor are interconnected devices to transmit torque, mainly teeth or splines.

 

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