Hydraulic downhole motor with diamond sliding support

FIELD: engines and pumps.

SUBSTANCE: motor includes a housing with a rotor arranged inside it, the rotation of which is performed by the fluid medium supplied with a pump, as well as a spindle housing with a shaft arranged inside it, which is installed on radial and axial sliding supports. The spindle shaft is attached to the motor rotor and a bit. Some amount of fluid medium is pumped through radial and axial sliding supports, and axial support of the spindle is made in the form of two pairs of rotor and stator rings with an annular row of thrust modules, which is fixed in each of them. Stator rings are fixed in the spindle housing, rotor rings are installed on the spindle shaft, and each thrust module includes layers of polycrystalline diamonds on the edge facing the edges of adjacent modules, and contacts in turn with one or two edges of adjacent modules. The motor includes a splined bush with external splines, which is installed on the spindle shaft, and two elastic damping supports arranged on the edges of the splined bush and receiving axial forces acting on the axial support of the spindle. Each elastic damping support contacts the rear edge of the corresponding rotor ring with the fixed annular row of thrust modules, and rotor rings with annular rows of thrust modules fixed in them are provided with internal splines corresponding to external splines of the splined bush, and each of them is installed with possibility of annular distortion of the rotor ring with the annular row of thrust modules, which is fixed in it, relative to its own elastic damping support.

EFFECT: increasing service life and improving reliability of the axial sliding support of the spindle of the hydraulic downhole motor with thrust modules; improving accuracy of curvature parameters of the well shaft; enlarging the hole boring per bit run using hydraulic jars in the tubing; increasing the increase rate of curvature parameters of wells, and reducing stresses in the layout of the bottom of the drill column and downtime of the drilling unit.

6 cl, 5 dwg

 

The invention relates to devices for rotational drive placed in the borehole, and can be used in hydraulic gyratory propeller engines and turbodrills for rotation of the rotor from the pumping fluid abrasive media, in particular, with diamond axial sliding bearing spindle, provided with a drilling bit for drilling directional and horizontal oil and gas wells.

Known hydraulic downhole motor with a diamond thrust bearing, comprising a housing spindle, placed inside the shaft, mounted on the radial and axial bearing slides, fixed on the shaft of the bit, with some fluid pumped through the radial and axial sliding bearing and the axial bearing is made in the form of two pairs of rotor and stator rings are fixed in each of them next thrust modules, each pair of rotor and stator ring stator ring fixed in the housing of the spindle, the rotary ring is bonded to the shaft of the spindle, and each thrust module contains a layer of polycrystalline diamond on the end facing to the adjacent ends of the thrust modules, and in turn is in contact with one or two ends of the above-mentioned resistant modules (US 4620601, 04.11.1986).

A disadvantage of the known hydraulic downhole motor with thrust modules containing layers policriti the " diamond PDC (Polycrystalline Diamond Compakt) at the ends, facing the adjacent ends of the thrust modules, is incomplete, the possibility of increasing the life and reliability of the axial sliding bearing spindle, pumped and pump fluid abrasive media (mud)that is explained by the narrow range of adjustment and compression of the Belleville springs 111 (within 2÷3 mm), the failure of spherical rings 112, 114 and the Belleville springs 111 due to Slovenia cavity Belleville springs 111 and the hollow spherical rings 112 and 114 abrasive particles: up to 2% of the sand with dimensions of 0.15÷0,95 mm and up to 5% of oil products, for example, in polymer-clay mud density of 1.16÷1.26 g/cm3shown in figure 2.

The disadvantages of the known downhole motor incomplete due the possibility of "self-talk" stator rings in the housing of the spindle or the rotary ring on the shaft of the spindle to ensure the parallelism between working surfaces of the thrust modules, containing layers of polycrystalline diamond on the ends, with the appearance of a gap in the lower radial bearing of the sliding spindle caused by bending of the spindle shaft with the bit when drilling a curved borehole, which leads to high local compression stress on the contacting end faces of the thrust modules, containing layers of polycrystalline diamond crystals, vibrations, "sticking" and the destruction of the axial oprisoreanu.

A disadvantage of known construction with persistent modules containing layers of polycrystalline diamond on the ends, is also incomplete, the possibility of increasing the life and reliability of the pumped mud axial sliding bearing spindle, which is explained by insufficient strength of the support rings and pins (POS. 116, 117, 118, 119, C, 117S)are destroyed when the maximum axial load from the bit pointing from the bottom to the mouth of the well, with the change of sign of the axial load acting on the axial sliding bearing, due to Slovenia abrasive particles: up to 2% of the sand with dimensions of 0.15÷0,95 mm and up to 5% of oil products, for example, in polymer-clay mud density of 1.16÷1.26 g/cm3in the cavity of the rings s, 117S, shown in figure 2.

The disadvantage of known construction due to the large value of the stress ratio of the axial sliding bearing in the spindle body (Stress ratio, the ratio of variable amplitude voltage to the average voltage), essentially equal to 8÷10, and a high probability of occurrence of vibrations, ' frozen ' and fracture of polycrystalline diamond crystals in the axial bearing of the slide when using the engine in a horizontal driven layouts of the bottom of the drill string, in the areas of curvature inclined direction well.

Known hydraulic the cue downhole motor with a diamond sliding bearing, containing the motor housing placed inside the rotor, the rotation of which is pumping flow of fluid, and the spindle body placed inside the shaft mounted on the radial and axial bearing of the slide, a spindle shaft connected with the rotor of the motor and bit, with some fluid pumped through the radial and axial sliding bearing and the axial bearing of the spindle is made in the form of two pairs of rotor and stator rings are fixed in each of them a ring next thrust modules, the stator ring is bonded with the spindle body, a rotary ring fastened to the shaft of the spindle, and each thrust module contains a layer of polycrystalline diamond on the end facing the end faces of adjacent modules, and in turn is in contact with one or two ends of adjacent modules (US 4560014, 24.12.1985).

A disadvantage of the known hydraulic downhole motor with thrust modules, containing layers of polycrystalline diamond PDC (Polycrystalline Diamond Compakt) at the ends facing the adjacent ends of the thrust modules, is incomplete, the possibility of increasing the life and reliability of the axial sliding bearing spindle, pumped and pump fluid abrasive media (mud)that is explained by the narrow range of adjustment and compression of the Belleville springs 76 (within 2÷3 mm), refusal to work the Belleville springs 76 due to Slovenia abrasive particles: up to 2% of the sand with dimensions of 0.15÷0,95 mm and up to 5% of oil products, for example, in polymer-clay mud density of 1.16÷1.26 g/cm3in the cavity of the Belleville springs 76, shown in figure 2.

The disadvantages of the known downhole motor incomplete due the possibility of "self-talk" stator rings in the housing of the spindle or the rotary ring on the shaft of the spindle to ensure the parallelism between working surfaces of the thrust modules, containing layers of polycrystalline diamond on the ends, with the appearance of a gap in the lower radial bearing of the sliding spindle caused by bending of the spindle shaft with the bit when drilling a curved borehole, which leads to high local compression stress on the contacting end faces of the thrust modules, containing layers of polycrystalline diamond crystals, vibrations, "sticking" and the destruction of the axial sliding bearing.

When the valid bit load (40000 kgs) Belleville springs 76 are compressed to the stop face of the teeth 66, 67 in the axial modules 64, 68, do not provide "self-talk" and the parallelism between working surfaces 77, containing layers of polycrystalline diamond PDC in a persistent modules 29 and 68, 38 and 64 relative to each other, which leads to high local compression stress on the contacting end faces 77 of the thrust modules 29 and 68, 38 and 64, causes vibrations, "sticking" and the destruction of the axial sliding bearing is shown is figure 2.

The disadvantages of the known constructions with persistent modules containing layers of polycrystalline diamond on the end faces of the thrust modules, facing toward the adjacent ends of the thrust modules are explained essentially by the appearance of a gap in the lower radial bearing of the sliding spindle when drilling curved boreholes caused by bending of the spindle shaft with a chisel, which leads to the deviation from parallelism of the rotor and stator rings, thrust modules, high local compression stress on the contacting end faces of the thrust modules, containing layers of polycrystalline diamond crystals, vibrations, "sticking" and the destruction of the axial sliding bearing.

A disadvantage of the known construction is also incomplete, the possibility of increasing the life and reliability of the pumped mud axial sliding bearing spindle hydraulic downhole motor, because of the low fatigue endurance of the Belleville springs 76, insufficient strength resistant modules (POS. 64, 68, 28, 38), which would be destroyed if the maximum axial loads from the bit directed from the bottom to the mouth of the well, due to Slovenia abrasive particles in the axial bearing of the slide, "sticking" and fracture of polycrystalline diamond crystals in the axial bearing of the slide, the spring disc spring package is in 76 of the thrust module (POS. 64, 68, 28, 38, 29, 33) when the ingress of abrasive particles: up to 2% of the sand with dimensions of 0.15÷0,95 mm and up to 5% of the oil contained, for example, in polymer-clay mud density of 1.16÷1.26 g/cm3on the surface 79, 83, 84 polycrystalline diamond in the inserts 77, 78, essentially, with the change of sign of the action of the axial load on the bit during drilling.

The disadvantage of known construction due to the large value of the stress ratio of the axial sliding bearing in the spindle body (Stress ratio, the ratio of variable amplitude voltage to the average voltage), essentially equal to 9÷11, and a high probability of occurrence of vibrations, ' frozen ' and fracture of polycrystalline diamond crystals in the axial bearing of the slide when using the engine in a horizontal driven layouts of the bottom of the drill string, in the areas of curvature inclined direction well.

It is not possible to compensate for positive and negative emissions dynamic variation of axial load on the bit and to maintain an optimal axial load on the bit by saving the current values of the axial loads without buckling directed obliquely angled the drill pipe string and provide the parameters of the curvature of the wellbore.

Known hydraulic layout C is the Boyne engine for drilling subterranean formations creates a torque on the drill bit, the motor is attached to a thrust bearing including a first node having multiple support members that define a first bearing surface, at least one supporting element from a set of supporting elements of the first node that includes a polycrystalline diamond plate on the substrate, the second node having multiple support elements defining a second bearing surface, the first bearing surface and second bearing surface are configured to form an engagement between them during the relative displacement of the first node and the second node, the first flexible element located between the first node and at least one support element of the first node, the first flexible element having such a configuration to provide the desired amount of displacement, at least one support element of the first node in the first direction relative to the first node, and a second flexible element located between the first node and at least one support element of the first node, the second flexible element having such a configuration to provide the desired amount of displacement, at least one support element of the first node in the second direction relative to the first node, while the second direction design the e from the first direction (US 7946768, 24.05.2011).

In a known arrangement of hydraulic downhole motor for drilling subterranean formations, the axial support device includes at least a first flexible element or the second flexible element, which has such a configuration to provide the desired amount of deviation of a surface, at least one support element of the first node within ±2 degrees, and also includes a bias element includes attached to the bottom of bias item wavy spring washer, curved spring washer or a Belleville spring washer, and the bias element is configured to move at least one required supporting element, at least in one of the following directions: radial direction, the annular direction, longitudinal direction.

A disadvantage of the known hydraulic downhole motor with thrust modules, containing layers of polycrystalline diamond on the end facing the adjacent ends of the thrust modules, is incomplete, the possibility of increasing the life and reliability of the axial sliding bearing spindle, pumped and pump fluid abrasive media, which is explained by the device axial sliding bearing, which includes attached to the bottom of the wavy spring washer, curved spring washer or Belleville spring Sha is Boo, having a narrow range of adjustment and compression, essentially, in the range of 2÷3 mm, shown in Fig.

When the valid bit load (40000 kgf) axial bearing slides, which includes attached to the bottom of the wavy spring washer, curved spring washer or Belleville spring washer shown in Fig shrinks until it stops and does not provide damping of the axial forces from the drill bit operating at the specified axial sliding bearing, does not provide "self-talk" and the parallelism between working surfaces of the thrust modules relative to each other, which leads to high local compression stress on the contacting end faces of the above-mentioned thrust modules, containing layers of polycrystalline diamond, vibrations, "sticking" and the destruction of the axial sliding bearing.

The disadvantages of the known constructions with persistent modules containing layers of polycrystalline diamond on the end faces of the thrust modules, each of which includes attached to the bottom of the wavy spring washer, curved spring washer or a Belleville spring washer, explains the full grip attached to the bottom of the thrust modules wavy spring washers, curved spring washers or Belleville spring washers, and the appearance of a gap in time in the lower radial bearing of the sliding spindle, vyzyvae the CSOs by the bending of the spindle shaft with the bit when drilling a curved borehole, which leads to the deviation from parallelism of the rotor and stator rings, thrust modules, containing layers of polycrystalline diamond on the end faces of the thrust modules, facing toward the adjacent ends of the thrust modules axial sliding bearing, does not provide "self-talk" working surfaces of the thrust modules relative to each other.

Closest to the claimed design is a hydraulic downhole motor with a diamond sliding bearing, comprising a housing of the motor placed inside the rotor, the rotation of which is pumping flow of fluid, and the spindle body placed inside the shaft mounted on the radial and axial bearing of the slide, a spindle shaft connected with the rotor of the motor and bit, with some fluid pumped through the radial and axial sliding bearing and the axial bearing of the spindle is made in the form of two pairs of rotor and stator rings are fixed in each of them a ring next thrust modules, the stator ring is bonded with the body spindle, a rotary ring fastened to the shaft of the spindle, and each thrust module contains a layer of polycrystalline diamond on the end facing the end faces of adjacent modules, and in turn is in contact with one or two ends of adjacent modules, with each pair of rotor and stator rings chilopora modules rotary ring is one less than the number of resistant modules stator ring, the area of the orifice for the fluid between each thrust modules rotary rings in contact with each thrust module stator ring is 1,154÷1,618 from the cross-section area for the fluid between each thrust modules stator rings in contact with each thrust module rotary ring, the height H of each of the thrust module with height Z of the rotor and stator rings connected by the relation N=(0,255÷0,355)Z (EN 2340757, 10.12.2008).

A disadvantage of the known designs of hydraulic downhole motor with thrust modules, containing layers of polycrystalline diamond on the ends facing the adjacent ends of the thrust modules, is incomplete, the possibility of increasing the life and reliability of the axial sliding bearing spindle, pumped and pump fluid abrasive media (mud), which is explained by the rigid mounting of the rotor and the stator rings are fixed in each of them next thrust modules in packages in the housing and on the shaft of the spindle, essentially due to the lack of "self" rotary rings in the body of the spindle or shaft of the spindle to compensate for angular misalignment and ensure the parallelism between working surfaces persistent modules containing layers of polycrystalline diamond on the ends.

The disadvantages of the known downhole motor is yasnyayutsya incomplete "self" stator rings in the housing of the spindle or the rotary ring on the shaft of the spindle to ensure the parallelism between working surfaces of the thrust modules, contains layers of polycrystalline diamond on the ends, with the appearance of a gap in the lower radial bearing of the sliding spindle caused by bending of the spindle shaft with the bit when drilling a curved borehole, which leads to high local compression stress on the contacting end faces of the thrust modules, containing layers of polycrystalline diamond crystals, vibrations, "sticking" and the destruction of the axial sliding bearing.

The technical problem on which the invention is directed, is to increase the life and reliability of the axial sliding bearing spindle hydraulic downhole motor with thrust modules, containing layers of polycrystalline diamond on the sides facing the ends of adjacent modules by mounting on the shaft of the spindle splined sleeve with external slots and two provedeniya supports in contact with the rear ends of the rotary rings with internal splines corresponding to the external splines of the splined sleeve, to compensate for angular misalignment and ensure the parallelism between working surfaces of the thrust modules, containing layers of polycrystalline diamond on the ends.

The essence of the technical solution is that the hydraulic downhole motor with a diamond sliding bearing, comprising a housing of the motor placed inside the ro is or, rotation which is a pumping flow of fluid, and the spindle body placed inside the shaft mounted on the radial and axial slide bearing, a spindle shaft connected with the rotor of the motor and bit, with some fluid pumped through the radial and axial sliding bearing and the axial bearing of the spindle is made in the form of two pairs of rotor and stator rings are fixed in each of them a ring next thrust modules, the stator ring fixed in the housing of the spindle, a rotary ring mounted on the shaft of the spindle, and each thrust module contains layers of polycrystalline diamond on the end, facing toward the ends adjacent modules, and in turn is in contact with one or two ends of adjacent modules, according to the invention contains mounted on a shaft splined sleeve with external slots and two providentiae reliance placed on the edges of the slotted sleeve and withstand axial forces acting on the axial bearing spindle, made in the form of two pairs of rotor and stator rings are fixed in each of them a ring next thrust modules with polycrystalline diamond layers, with each providentia bearing contact with the rear end of the respective rotary ring with the assigned ring near the thrust modules, and a rotary ring C is enshrined in them ring rows resistant modules made with internal splines, the respective outer slotted slotted bushings, and installed, each with the possibility of angular misalignment of the rotary ring with the assigned ring near the thrust modules on their providential support.

Each providentia bearing ring formed by the belt edge slotted sleeve, the support ring bushing end wall mounted on the shaft of the spindle and in contact with the slotted end of the sleeve, and an annular thrust bearing disposed between the ring belt region slotted sleeve and the inner annular zone supporting an annular sleeve forming inside the closed chamber, in which is a ring of resilient elastomeric material, is tightly in contact with the walls of the specified closed chamber, with an annular thrust bearing is installed with the possibility of angular misalignment together with the rotary ring with the assigned ring near the thrust of the modules relative to the axis of rotation of the spindle within ±3 degrees.

Mounted on the periphery splined sleeve two providentiae supports are located along the axis of the spindle shaft is mirrored relative to each other.

The area of the F ring of resilient elastomeric material, is placed in a closed chamber providential supports, and area F1persistent modules containing layers of polycrystalline Almazova end of the thrust modules, fixed in the rotary ring, connected by the relation: F=(1,35÷1,75)F1.

A ring of resilient elastomeric material, is placed in a closed chamber providential support, has a hardness of 80±3% shore A.

On the end ring of resilient elastomeric material, is placed in a closed chamber providential support made the annular protrusion is in contact with the end of the annular thrust bearing.

The performance of hydraulic downhole motor with a diamond sliding bearing so that it contains mounted on a shaft splined sleeve with external slots and two providentiae reliance placed on the edges of the slotted sleeve and withstand axial forces acting on the axial bearing spindle, made in the form of two pairs of rotor and stator rings are fixed in each of them a ring next thrust modules with polycrystalline diamond layers, with each providentia bearing contact with the rear end of the respective rotary ring with the assigned ring near the thrust modules, and a rotary ring mounted in their ring rows resistant modules made with internal slots corresponding to the outer slotted slotted bushings, and installed, each with the possibility of angular misalignment of the rotary ring with the assigned ring near the thrust module is th on their providential support, increases the life and reliability of the axial sliding bearing spindle hydraulic downhole motor with thrust modules, containing layers of polycrystalline diamond on the sides facing the ends of adjacent modules by mounting on the shaft of the spindle splined sleeve with external slots and two provedeniya supports in contact with the rear ends of the rotary rings with internal splines corresponding to the external splines of the splined sleeve, to compensate for angular misalignment and ensure the parallelism between working surfaces of the thrust modules, containing layers of polycrystalline diamond on the ends, prevents vibration, "tacks" and fracture of polycrystalline diamond crystals in the working friction surfaces of the axial sliding bearing spindle drill.

The advantages of the proposed design with thrust modules, containing layers of polycrystalline diamond on the end faces of the thrust modules, facing toward the adjacent ends of the thrust modules, due essentially to compensate for the distortions and deviations from parallelism of the rotor and stator rings, thrust modules, containing layers of polycrystalline diamond on the end faces of the thrust modules, facing toward the adjacent ends of the thrust modules axial sliding bearing is caused by the occurrence of radial clearance in the lower radial bearing of the sliding spindle is when drilling directional and horizontal wells due to the bending of the spindle shaft with the bit when drilling a curved borehole.

This embodiment, for example, gyratory screw hydraulic motor with diamond axial sliding bearing spindle increases the accuracy of drilling directional and horizontal oil and gas wells, and improve technical and economic performance drilling: increases the sinking of wells for the flight of the bit, which reduces the downtime of the rig.

The performance of hydraulic downhole motor with a diamond sliding bearing so that each providentia bearing ring formed by the belt edge slotted sleeve, the support ring bushing end wall mounted on the shaft of the spindle and in contact with the slotted end of the sleeve, and an annular thrust bearing disposed between the ring belt region slotted sleeve and the inner annular zone supporting an annular sleeve forming inside the closed chamber, in which is a ring of resilient elastomeric material, is tightly in contact with the walls of the specified closed chamber, with an annular thrust bearing is installed with the possibility of angular misalignment together with the rotary ring with fixed therein the ring near the thrust of the modules relative to the axis of rotation of the spindle within ±3 degrees, simplifies the design providential support, provides economic benefits by reducing the possible value of the axial sliding bearing with thrust modules, contains layers of polycrystalline diamond, with each providentia bearing perceives axial forces acting on its own axial sliding bearing spindle, and compensates for distortions and deviations from parallelism own rotary ring connected with torque transfer with slotted sleeve mounted on the shaft of the spindle, which also increases the life and reliability in the pumped mud axial bearing of the sliding spindle hydraulic downhole motor.

The performance of hydraulic downhole motor with a diamond sliding bearing so that are installed on the edges of the slotted sleeve two providentiae supports are located along the axis of the spindle shaft is mirrored relative to each other, the area of the F ring of resilient elastomeric material, is placed in a closed chamber providential supports, and area F1persistent modules containing layers of polycrystalline diamond on the end face of the thrust modules, mounted in the rotary ring, connected by the relation: F=(1,35÷1,75)F1while a ring of resilient elastomeric material, is placed in a closed chamber providential support, has a hardness of 80±3 units shore a, And on the end ring of resilient elastomeric material, is placed in a closed chamber providential support, done the n annular protrusion, contact with the end of the annular thrust bearing provides maximum permissible load on the bit is equal to F=40000 kg, increases the reliability of the design, eliminates axial play of the spindle shaft with a chisel through a predefined axial tension in provedeniya supports, increases the service life of the spindle bearings, at least until the resource bit with the teeth of the polycrystalline diamonds.

Performance providential support is confirmed by the calculation of the strength of the supporting annular sleeve with an end wall mounted on the shaft of the spindle and in contact with the slotted end of the sleeve limiting the compression ring of resilient elastomeric material, such as rubber IRP-1226-5, in a confined space.

Material supporting an annular sleeve end wall and parts of the connection providential support - steel HIM, GOST 4543-71.

Properties:

the tensile strength ofσin=930 MPa=95 kgf/mm2
yield strengthσ02=780 MPa=79,6 kgf/mm2
the fatigue limit at symmetric
cycle of loading (bending)σ-1=45,6 kgf/mm2
the permanent elongation at breakδ=13%
residual narrowing at breakψ=45%
the modulus of elasticityE=19800 MPa=20000 kgf/mm2

When the axial load ring of resilient elastomeric material in a confined space behaves like a liquid. Pressure in tires, resulting from axial compression of the rubber rings, causes tensile stresses in the support ring sleeve end wall mounted on the shaft of the spindle and in contact with the end of the slotted sleeve. When the valid bit load F=40000 kN rubber causes the pressure p=F/S=40000/113=354 kg/cm2where S=113 cm2square rubber ring. To simplify the calculation, a skirt supporting ring sleeve end wall taken in the form of dimensionless pipe under pressure. Of the tensile stresses in the skirt supporting ring sleeve end wall σp=p×rcf/h=354×9,05/0,7=4576 kg/cm2where rcf- the average radius of the wall of skirt supporting ring bushing, h is the wall thickness of skirt supporting ring sleeve.

For steel steel HIM, GOST 4543-71, yield:

σ02=780 MPa=79,6 kgf/mm2, σ02≥7000 kgf/cm2. Factor k=1.5.

With the consideration of the m, that end wall supporting an annular sleeve performs the function of a frame, the tensile stresses in the skirt supporting ring sleeve will be even less, with the strength of the support ring bushing end wall is sufficient.

The calculation of the stress-strain state of axial diamond sliding bearing and providential support, carried out by the finite element method with certified analytical software product ANSYS 12.1 static nonlinear formulation using elements, simulating the contact interaction, taking into account the elastic-plastic material properties, and the properties of rubber in a confined space design, showed that in the case of load balancing two pairs of rotor and stator rings are fixed in each of them a ring next thrust modules, each of which contains layers of polycrystalline diamond ARS (EN) grain 2000/1600 μm, forming a film composite with a thickness of 2.25 mm on the end facing the end faces of adjacent modules, and in turn is in contact with one or two ends of adjacent modules, margin limit the contact strength of the axial sliding bearing is 1.45, margin tensile strength providential support is 1.55V, the stress ratio of the axial sliding bearing in the spindle body (Stress ratio, the ratio and the changing amplitude of the voltage to the average voltage) is 2.3÷4,2.

The invention can be used in hydraulic gyratory propeller engines for drilling directional and horizontal oil and gas wells, as well as for drilling wells using mud motor.

Below hydraulic turbodrill T3 240 PC 801 diamond axial sliding bearing spindle, provodeniye supports for rotary ring with thrust modules, and a chisel.

1 shows a hydraulic turbo-drill with carbide radial sliding bearing spindle, diamond axial sliding bearing spindle, provodeniye supports for rotary ring with thrust modules, radial elastomeric bearings slip of the rotor of the mud motor with speed blades and chisels.

Figure 2 shows the element I in figure 1 of the spindle shaft with provodeniye bearings for axial sliding bearing is made in the form of a rotary ring with thrust modules, containing layers of polycrystalline diamond on the ends.

Figure 3 shows a section a-a in figure 2 across the thrust modules axial sliding bearing in the spindle body, containing layers of polycrystalline diamond on the ends.

Figure 4 shows the element II in figure 2 providential support to the rotor rings with persistent modules containing layers of polycrystalline diamond on the ends.

Figure 5 shows a ring is elastomeric material with the annular protrusion, designed for installation in a closed chamber providential support.

Hydraulic turbo-drill with a diamond sliding bearing includes a housing 1 turbodrill with 150 steps 2 stator blades 3 attached in the specified body 1 is placed inside the rotor 4 of the turbodrill with respectively 150 5-speed rotary blades 6 mounted on the shaft 7 of the rotor 4 of the mud motor, the rotation speed 5 rotor blades 6 is carried out and pump the fluid abrasive media 8 (mud), and includes a housing 9 spindle bearings placed inside the shaft 10 spindle mounted on tungsten carbide radial bearing 11 and axial sliding bearing 12 slip placed inside the housing 1 of the turbodrill while the shaft 7 of the rotor 4 of the turbodrill is set to 5 radial elastomeric bearings 13 slide mounted inside the housing 1 of the turbodrill, shown in figure 1.

The spindle shaft 10 is bonded thread 14 with the shaft 7 of the rotor 4 of the turbodrill and bonded thread with 15-bit sub 16 and the bit 17, and the portion of the fluid 8 flows for cooling and lubrication through radial elastomeric bearing 13 of the slip of the rotor 4 of the turbodrill, the open axial diamond bearing 12 slides, as well as through the radial bearing 11 of the sliding shaft 10 of the spindle, reinforced solid alloy TTC shown in figure 1.

In drilling Rast is a PR 8, radial bearings 13 of the slip of the rotor 4 of the turbodrill and an open axial diamond anvil 12 sliding in the housing 9 of the spindle, and carbide radial bearing 11 of the sliding shaft 10 spindle contains abrasive particles that have passed through the filters of the drill string: up to 2% of the sand with dimensions of 0.15÷0,95 mm and up to 5% of oil products, for example, in polymer-clay mud density of 1.16÷1.26 g/cm3.

Case 1 turbodrill bonded thread 18 19 sub intended for the fastening of the stator 150 degrees 2 blades 3, sub 19 is bonded thread 20 and tube 21 sub, and pipe sub 21 is bonded thread 22 with the column of drill pipe 23, as shown in figure 1.

The axial bearing 12 of the sliding spindle made in the form of two pairs of rotor and stator rings: rotary rings 24, 25 and stator rings 26, 27 are fixed in each of them a ring next thrust modules 28, the stator ring 26, 27 fixed in the housing 1 spindle, rotary rings 24, 25 are mounted on the spindle shaft 10, and each thrust module 28 contains layer 29 of polycrystalline diamond on the end face 30 facing the end faces 31 of adjacent modules 28, and in turn is in contact with one or two ends 31 of adjacent modules 28, shown in figures 1, 2, 3, 4.

Layers 29 on the ends 30, 31 of the thrust modules 28 are equipped with synthetic polycrystalline diamonds, for example, ARC (EN) grain is stotu 2000/1600 μm, forming a multilayer composite with a thickness of 2.25 mm, shown in figure 4.

Layers 29 on the ends 30, 31 of the thrust modules 28 can be equipped with polycrystalline diamond PDC, for example, US firms Synthetic (US) grain 2000/1600 μm, forming a multilayer composite thickness of 2.05 mm, shown in figure 4.

Hydraulic turbo-drill with a diamond sliding bearing contains mounted on the shaft 10 of the spindle splined sleeve 32 with external slots 33, 34 and two providentiae supports 35 and 36 placed on the edges 37 and 38 respectively splined sleeve 32, perceiving axial forces acting on the axial bearing 12 of the spindle, which is made in the form of two pairs of rotor and stator rings: rotary rings 24, 25 and stator rings 26, 27 are fixed in each of them a ring next thrust modules 28, the stator ring 26, 27 fixed in the housing 1 of the spindle, the rotary ring 24, 25 is installed on the shaft 10 of the spindle, and each thrust module 28 contains layer 29 of polycrystalline diamond on the end face 30 facing the end faces 31 of adjacent modules 28, and in turn is in contact with one or two ends 31 of adjacent modules 28, shown in figures 1, 2, 3, 4.

Providentia bearing 35 is in contact with the rear end 39 of the rotary ring 24 with a fixed ring near the thrust modules 28, and the rotary ring 24 mounted in their ring rows resistant modules 28 are made from inside them slots 40, the corresponding external splines 33 splined sleeve 32, and is installed with the possibility of angular misalignment of the rotary ring 24 with a fixed ring near the thrust modules 28 with respect to its own providential support 35, as shown in figure 2, 3, 4.

Providentia bearing 36 is in contact with the rear end face 41 of the rotary ring 24 with a fixed ring near the thrust modules 28, and the rotary ring 24 mounted in their ring rows resistant modules 28 are made with internal splines 42, the corresponding external splines 34 splined sleeve 32, and is installed with the possibility of angular misalignment of the rotary ring 24 with a fixed ring near the thrust modules 28 with respect to its own providential support 36 shown in figures 1, 2, 3, 4.

Each providentia bearing, for example providentia bearing 35, is formed an annular belt edge 43 37 splined sleeve 32, the supporting ring sleeve 44 with the end wall 45 mounted on the shaft 10 of the spindle and in contact with the end face (edge) 37 splined sleeve 32, and annular thrust bearing 46 disposed between the ring belt 43 of the edge (end) 37 splined sleeve 32 and the inner annular zone 47 of the supporting annular sleeve 44 formed inside the closed chamber 48 in which is a ring 49 of resilient elastomeric material, such as rubber IRP-1226-5, photoconductive with the walls of the specified closed chambers: the ring belt edge 43 37 splined sleeve 32, with the inner ring zone 47 of the supporting annular sleeve 44, with the end wall 45 of the supporting annular sleeve 44 and the rear surface 50 of the annular thrust bearing 46, as shown in figure 2, 4.

When this annular thrust bearing 46 is installed with the possibility of angular misalignment (due to the radial clearance or spherical zones) together with the rotary ring 24 with a fixed ring near the thrust modules 28 containing layers 29 of polycrystalline diamond on the end faces 30, about the axis of rotation of the shaft 51 10 spindle within ±3 degrees, as shown in figure 2, 4.

Installed on the edges 37 and 38 splined sleeve 32 two providentiae supports 35 and 36 are arranged along the axis 51 of the shaft 10 of the spindle mirror relative to each other, as shown in figures 1, 2, 4.

Area 52, F ring 49 of resilient elastomeric material, such as rubber IRP-1226-5 placed in a closed chamber 48 providential support, for example, 35, and area 53, F1persistent modules 28 containing layers 29 of polycrystalline diamond on the end face 30 of the thrust modules 28, fixed in the rotary ring 24, connected by the relation: F=(1,35÷1,75)F1shown in figure 3, 4, 5. The ring 49 of resilient elastomeric material, such as rubber IRP-1226-5 placed in a closed chamber 48 providential support, for example, 35, has a hardness of 80±3% shore As shown in figure 3, 4.

At the end of the ring 4 of resilient elastomeric material, for example, rubber IRP-1226-5 placed in a closed chamber 48 providential support, for example, 35, made the annular protrusion 54 that is designed to create a preset axial preload in contact with the rear surface 50 of the annular thrust bearing 46, shown in figure 4, 5.

Hydraulic turbodrill T3 240 PC 801 with provodeniye supports for rotary axial rings diamond sliding bearing spindle with a chisel works as follows: the flow of drilling fluid 8 containing abrasive particles, for example up to 2% of the sand with dimensions of 0.15÷0,95 mm and up to 5% of the oil contained in the polymer-clay mud density of 1.16÷1.26 g/cm3under the pressure of 37÷45 MPa for the string of drill pipe 23 is fed into the housing 1 of the turbodrill, containing 150 degrees 2 stator blades 3 attached in the specified block 1, placed inside the rotor 4 of the turbodrill with respectively 150 5-speed rotary blades 6 mounted on the shaft 7 of the rotor 4 of the turbodrill, creates a torque on 150 5 speed rotary blades 6 mounted on the shaft 7 of the rotor 4 of the turbodrill, passed forth on the shaft 10 of the spindle, the drill bit sub 16 and the drill bit 17, performs the rotation of the drill bit 17 and drilling.

Part of the fluid 8 is pumped under pressure 37÷45 MPa through radial elastomeric bearing 13 slip corrobora, open axial diamond bearing 12 slides, as well as through the radial bearing 11 of the sliding shaft 10 of the spindle, reinforced with hard metal.

With the appearance of a gap in the radial bearing 11 of the sliding shaft 10 of the spindle, reinforced with hard metal, caused by bending of the shaft 10 of the spindle with bit 17 when drilling in hard and hard rock curved borehole, providentia bearing 35 is in contact with the rear end 39 of the rotary ring 24 with a fixed ring near the thrust modules 28, and the rotary ring 24 mounted in their ring rows resistant modules 28 are made with internal splines 40, the corresponding external splines 33 splined sleeve 32, and is installed with the possibility of angular misalignment of the rotary ring 24 with a fixed ring near the thrust modules 28 with respect to its own providential support 35, and provides compensation for angular misalignment and parallel working surfaces of the thrust modules, containing layers of polycrystalline diamond on the ends, which reduces the local compressive stress on the contacting end faces of the thrust modules, prevents vibrations, "sticking" and the destruction of the axial sliding bearing.

With the appearance of a gap in the radial bearing 11 of the sliding shaft 10 of the spindle, reinforced with hard metal, caused by bending of the shaft 10 spindle drill 17 Buren is in a strong and solid rocks of the curved borehole, providentia bearing 36 is in contact with the rear end face 41 of the rotary ring 24 with a fixed ring near the thrust modules 28, and the rotary ring 24 mounted in their ring rows resistant modules 28 are made with internal splines 42, the corresponding external splines 34 splined sleeve 32, and is installed with the possibility of angular misalignment of the rotary ring 24 with a fixed ring near the thrust modules 28 with respect to its own providential support 36, the axial bearing 12 of the sliding spindle, made in the form of two pairs of rotor and stator rings: rotary rings 24, 25 and stator rings 26, 27 mounted in each ring near the thrust modules 28, the stator ring 26, 27 fixed in the housing 1 spindle, rotary rings 24, 25 are mounted on the spindle shaft 10, and each thrust module 28 contains layer 29 of polycrystalline diamond on the end face 30 facing the end faces 31 of adjacent modules 28, and in turn is in contact with one or two ends 31 of adjacent modules 28, and provides compensation for angular misalignment and parallel working surfaces of the thrust modules, containing layers of polycrystalline diamond on the ends, which reduces the local compressive stress on the contacting end faces of the thrust modules, prevents vibration, "sticking" and the destruction of the axial sliding bearing.

When the imp is to turbodrill with diamond axial bearing 12 of the sliding spindle, provodeniye supports 35, 36 to the rotor rings 24, 25 with persistent modules 28 so that the area 52, F ring 49 of resilient elastomeric material, such as rubber IRP-1226-5 placed in a closed chamber 48 providential support, for example, 35, and area 53, F1persistent modules 28 containing layers 29 of polycrystalline diamond on the end face 30 of the thrust modules 28, fixed in the rotary ring 24, connected by the relation: F=(1,35÷1,75)F1the ring 49 of resilient elastomeric material, such as rubber IRP-1226-5 placed in a closed chamber 48 providential support, for example, 35, has a hardness of 80±3 units shore a, while the end ring 49 of resilient elastomeric material, such as rubber IRP-1226-5 placed in a closed chamber 48 providential support, for example, 35, made the annular protrusion 54 that is designed to create a preset axial preload in contact with the rear surface 50 of the annular thrust bearing 46, the value of the stress ratio of the axial sliding bearing in the spindle body (Stress ratio, the ratio changing the amplitude of the voltage to the average voltage) is reduced and is (2,3÷4,2), which reduces the chance of "sticking" and the destruction of the layers 29 on the ends 30, 31 of the thrust modules 28, equipped with polycrystalline diamonds in the axial bearing 12 of the sliding spindle.

When using the home is aamoi design increases the life and reliability of the axial sliding bearing spindle hydraulic downhole motor with thrust modules, contains layers of polycrystalline diamond on the sides facing the ends of adjacent modules, due to angular misalignment and ensure the parallelism between working surfaces of the thrust modules, improves the accuracy of the curvature parameters of the wellbore increases borehole drilling for the flight of the bit using the string of drill pipes, hydraulic jars, increases the rate of curvature parameters wells, reduced voltage in the layout of the bottom of the drill string and the downtime of the rig.

1. Downhole hydraulic motor with a diamond sliding bearing, comprising a housing of the motor placed inside the rotor, the rotation of which is pumping flow of fluid, and the spindle body placed inside the shaft mounted on the radial and axial slide bearing, a spindle shaft connected with the rotor of the motor and bit, with some fluid pumped through the radial and axial sliding bearing and the axial bearing of the spindle is made in the form of two pairs of rotor and stator rings are fixed in each of them a ring next thrust modules, the stator ring fixed in the housing of the spindle, a rotary ring mounted on the shaft of the spindle, and each thrust module contains layers of polycrystalline diamond on the end, facing toward the ends of Minich modules and alternately in contact with one or two ends of adjacent modules, characterized in that it contains mounted on a shaft splined sleeve with external slots and two providentiae reliance placed on the edges of the slotted sleeve and withstand axial forces acting on the axial bearing spindle, made in the form of two pairs of rotor and stator rings are fixed in each of them a ring next thrust modules with polycrystalline diamond layers, with each providentia bearing contact with the rear end of the respective rotary ring with the assigned ring near the thrust modules, and a rotary ring mounted in their ring rows resistant modules made with internal splines corresponding to the external splines of the splined sleeve, and installed, each with the possibility of angular misalignment of the rotary ring with the assigned ring near the thrust modules on their providential support.

2. Downhole hydraulic motor with a diamond sliding bearing according to claim 1, characterized in that each providentia bearing ring formed by the belt edge slotted sleeve, the support ring bushing end wall mounted on the shaft of the spindle and in contact with the slotted end of the sleeve, and an annular thrust bearing disposed between to icewm belt edge of the slotted sleeve and the inner annular zone supporting an annular sleeve, forming inside the closed chamber, in which is a ring of resilient elastomeric material, is tightly in contact with the walls of the specified closed chamber, with an annular thrust bearing is installed with the possibility of angular misalignment together with the rotary ring with the assigned ring near the thrust of the modules relative to the axis of rotation of the spindle within ±3°.

3. Downhole hydraulic motor with a diamond sliding bearing according to claim 1 or 2, characterized in that mounted on the periphery splined sleeve two providentiae supports are located along the axis of the spindle shaft is mirrored relative to each other.

4. Downhole hydraulic motor with a diamond sliding bearing according to claim 1 or 2, characterized in that the area of the F ring of resilient elastomeric material, is placed in a closed chamber providential supports, and area F1persistent modules containing layers of polycrystalline diamond on the end face of the thrust modules, mounted in the rotary ring, connected by the relation: F=(1,35÷1,75)F1.

5. Downhole hydraulic motor with a diamond sliding bearing according to claim 1 or 2, characterized in that a ring of resilient elastomeric material, is placed in a closed chamber providential support, has a hardness of 80±3% shore A.

6. Downhole hydraulic motor with a diamond pillar splits the supply according to claim 1 and 2, characterized in that on the end ring of resilient elastomeric material, is placed in a closed chamber providential support made the annular protrusion is in contact with the end of the annular thrust bearing.



 

Same patents:

FIELD: machine building.

SUBSTANCE: device includes frame 2, powder brake 3, kinematic chain A between outlet shaft of HBM 1 and rotor 4 of powder brake 3, hydraulic baffle plate 5, monitoring and testing unit 6 and date control and processing unit 7. Kinematic chain A is made in the form of gear-type conical multiplier 8 with coupling clutches 9, 10 in connections of its shafts 11 and 12 with outlet shaft B of HBM 1 and rotor 4 of powder brake 3. Hydraulic baffle plate 5 is made on cover plate 13 of multiplier 8 in the form of an annular reservoir enclosing with seal 14 the lower part of housing B of HBM 1.

EFFECT: improving accuracy and enlarging the HBM loading range at testing, and possibility of stand-alone use.

1 dwg

FIELD: machine building.

SUBSTANCE: invention is used for run-in and test of hydraulic bottomhole motor (HBM). When testing HBM 1, it is installed in a vertical position above well 2 of its further operation and attached to housing A by means of spinning wrench 3 on stationary drilling outfit 4 of well 2. Outlet shaft 5 of spindle 6 of HBM 1 is attached through coupling device 7 to inlet shaft 8 of multiplier 9 installed on rotary table 10. Rotation of rotor 11 with spindle 6 is performed by injection of working fluid to HBM 1 through adapter 12 of pump station 13 of drilling outfit 4 of well 2. Mechanical loading of outlet shaft 5 of spindle 6 is performed through multiplier 9 kinematically connected at its outlet shaft 15 to powder brake 17, with further measurement and analysis of revolutions and braking moments at the outlet of the latter, and flow rate and pressure of working fluid at HBM 1 inlet.

EFFECT: improving accuracy of the method and its approximation to HBM operating conditions.

1 dwg

FIELD: machine building.

SUBSTANCE: invention is used for run-in and test of hydraulic bottomhole motor (HBM). Bench includes drive device 2 having pump station 3, pressure line 4 and assembly 5 for attachment of HBM 1, loading device 6 having frame 7 and powder brake 8 kinematically connected to outlet end of HBM 1, monitoring and testing unit 9 and data control and processing unit 10. Loading device 6 is equipped with conical multiplier 11 with hollow inlet shaft 12 located normally to base 13 of frame 7. HBM 1 is installed in cavity 14 of inlet shaft 12 of multiplier 11 with outlet end with chisel 15 conjugated with half-coupling 16 made with cams A for chisel 15 at inlet shaft 12 of multiplier 11, the outlet shaft 17 of which is kinematically connected to rotor 19 of powder brake 8. Loading device 6 is fixed on rotary table 20 coaxially to inlet shaft 12 of multiplier 11. Drive device 2 is made in the form of a stationary drilling rig of well 21.

EFFECT: increase in testing accuracy and approximation of the bench design to HBM real operating conditions.

1 dwg

FIELD: machine building.

SUBSTANCE: screw hydraulic machine includes rotor and stator of screw shape without any elastomeric coating, which are installed with a gap. Stator is solid metal alloy ceramic or composite material. Rotor is directed on its ends with guide system to exclude direct contact to stator. In addition, rotor surface or stator surface have grooves.

EFFECT: improvement of screw machine design is provided.

16 cl, 7 dwg

FIELD: mining.

SUBSTANCE: invention relates to trilling equipment, particularly, to hydraulic motors at drill string bottom that define design motor angularity angle in inclined and horizontal oil wells. Regulator toothed coupling with internal lengthwise spline slots and teeth on face side directed toward curved tube adapter features inclined face on teeth side. Point in intersection between toothed coupling teeth central lengthwise axis with central lengthwise axis of its internal spline slots is located in coupling face on teeth side. Point of intersection between hollow curved shaft thread lengthwise axis and central lengthwise axis of said hollow tube adapter is located in face plane of toothed coupling on teeth side. Curved tube adapter has bearing segment site in cross-section of which located is the plane with point of intersection between central lengthwise axis of curved tube adapter connecting it with thread of hollow curved shaft and lengthwise central axis of curved hollow adapter thread for joint with spindle section body thread.

EFFECT: higher transmitted torque, longer life, higher reliability.

5 cl, 5 dwg

FIELD: machine building.

SUBSTANCE: test bench for hydraulic bottomhole motors (HBM) includes base 1, clamping devices 3 to fix HBM, pump 2, receiving service tank, braking disc device 4 with hydraulic clamp and hydraulic drive, braking moment sensor, control device, frame, brake calipers with hydraulic cylinders, brake disc, power shaft with fixed brake disc and rigidly attached to HBM outlet shaft. Braking disc device 4 includes support, at least two brake discs combined into a unit located inside the support on power shaft; the same number of pairs of calipers with hydraulic cylinders, which are rigidly connected to each other in each pair and enclosing each disc in the unit. Frame is movable and kinematically connected to brake calipers. Braking moment sensor is installed on the support opposite movable frame. Base 1 is made in the form of receiving service tank.

EFFECT: creation of general-purpose test bench with wide range of standard sizes of HBM without readjustment of the bench; increase in maximum braking torque moment, improvement of measurement accuracy and efficiency.

3 cl, 3 dwg

FIELD: oil and gas production.

SUBSTANCE: device comprises a spring-loaded stop element, an elastomer seat with guide ribs, collars with central holes, valve seats. The valve is installed in the nipple of the hinged joint or torsion bar of the spindle in a screw bottomhole motor, in which holes are made for possible passage of a working medium.

EFFECT: simplified design, higher reliability.

6 cl, 6 dwg

FIELD: engines and pumps.

SUBSTANCE: first section with left-and-right threaded ends is clamped in assembly chuck. Adapter with left-and-right threaded ends is screwed in said first section to make gap H equal to 15-20 mm. Second stator section is screwed on adapter second threaded end to make the gap identical to that of first section. Then, mounting appliance made up of core with screw surface fitting with that of sections to be jointed together is inserted through first section into second sections o that their screw surfaces are aligned. Gaps H with allowance of ±0.3 mm is are retained. With said screw surfaces of both sections jointed together, core is driven to second section end. Then, first section is released from aforesaid chuck to clamp core therein and to clamp adapter therein. Now, chuck is switched on so that its rotation is transferred to both sections. Sections are screwed on adapter toward each other unless gaps H are taken up and threads are tightened as required.

EFFECT: faster assembly.

2 cl, 2 dwg

FIELD: machine building.

SUBSTANCE: test bench comprises brake shaft running in bearings, lever case with lever arranged radially relative to shaft rotational axis. Shaft is arranged inside brake device 8 and lever case with lever arranged radially relative to shaft rotational axis. Brake device and lever case with lever arranged radially relative to shaft rotational axis are coupled and arranged between shaft bearings. Test bench incorporates force transducer with electric output signal to measure tangential force resulting from motor torque mounted between lever arranged radially relative to shaft rotational axis and frame at preset radial distance from shaft rotational axis. Test bench is equipped with shaft drive 54 coupled with motor. Besides, it comprises control unit 34 connected with computer 35 to output motor and bench parameters.

EFFECT: higher efficiency, accuracy of measurements, and reliability.

5 cl, 8 dwg, 1 tbl

FIELD: engines and pumps.

SUBSTANCE: proposed section consists of interconnected slidable tubular case and hollow shaft. Tubular case is made up of threaded tubular elements. Hollow shaft is made up of threaded hollow elements running in front and rear axial thrust bearings and fron and rear radial plane bearings. Mud fluid is forced through hollow shaft. Shaft front threaded hollow element has thread for bit. From seal module is arranged between front threaded tubular element and shaft fron threaded hollow element on bit thread side. Annular slidable piston with inner and outer seals is arranged between case and shaft. Tight oil chamber is made between front seal module, annular piston, case and shaft, while annular piston isolates tight oil chamber from that filled with mud fluid. Besides, it comprises extra threaded tubular element of the case that incorporates in-motor plain bearing arranged between front and rear thrust bearings. Shaft front hollow threaded element shank with bit thread is connected with said plain bearing. Fishing nut with front and rear thrust end is arranged between front thrust bearing end and shaft front threaded hollow element end on thread of the latter. Diameter of said nut exceeds that of front radial plain bearing. Note here that annular piston is arranged between its radial plain bearing and rear plain bearing to make unloading chamber filled with mud fluid. Holes are made in case threaded tubular element for discharging a portion of mud fluid via rear radial plain bearing radial gap and unloading chamber from the case.

EFFECT: higher reliability, longer life.

4 cl, 6 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

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

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

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

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

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 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

FIELD: drilling equipment, particularly for directional drilling, namely control devices adapted to control angle and reactive moment.

SUBSTANCE: control device has hollow central member and three hollow tubular noncoaxial members connected to hollow central member. Inner member is disposed in center between the first and the second members. The first and the second members are connected with inner members by threaded connection. The first member is connected to spindle by threaded coupling, the second member is attached to engine body by threaded coupling and central member is connected to inner member by spline. Each of central member and the first member are provided with sectional contact seats located from spindle connection side, wherein a pair of sectional contact seats arranged from either sides of meridional spindle plane in drilling string curvature plane are defined between central and the first members. Sectional contact seats defined between central and the first members are spaced a distance L from the nearest edges of sectional contact seats of central and the first members along central axis of the first member. The distance L is more or equal to spindle diameter D. Angular deviation of the sectional contact seat formed in the first member from meridian spindle plane in drilling string curvature plane is oppositely directed relative reactive drilling bit moment.

EFFECT: increased stability and angle of gerotor engine deflection and increased accuracy of non-uniform well bottom zone penetration.

2 cl, 10 dwg

FIELD: well drilling equipment, particularly bearings adapted to work in abrasive medium.

SUBSTANCE: radial bearing has body and shaft, as well as thrust collars secured in the body and spring-loaded holders arranged between the shaft and the body. Inserts with conical outer surfaces are located between the holders and the shaft so that inserts cooperate with the shaft and with inner surfaces of the holders. Radial bearing is made as two oppositely arranged blocks and as compression spring inserted in-between. Each block has stop member secured in the body and made as slotted bush. Inserts are arranged in the bush and may perform displacement in radial direction. Thrust collars have conical surfaces cooperating with outer surfaces of the inserts. Angles α at apexes of the cones defined by interacted conical surfaces of bearing support inserts, thrust collars and holders are correlated with friction coefficient μ of interacted surfaces as tg(α/2)≈μ. Insert surfaces cooperating with shaft surface may have coating of elastomeric or hard-alloy material. In accordance with the second embodiment surfaces of inserts, thrust collars and holders interacting one with another may have flat contact zones, which are inclined at (α/2) angle to longitudinal shaft axis.

EFFECT: increased operational reliability of radial bearing.

6 cl, 3 dwg

FIELD: oil and gas well drilling equipment with the use of hydraulic downhole motors.

SUBSTANCE: support-and-centering member is made as metal hub with blades connected to spindle connector. Spindle connector has support cone formed on outer surface thereof and adapted to provide rigid connection with metal hub from inner surface thereof. Support cone of the connector is formed from side of conical thread connecting spindle body with connector. Spindle connector has splines to connect thereof with metal hub. Metal hub is pressed with pressing cone, retaining washer and nut from another side thereof. Metal hub may be installed concentrically or eccentrically to spindle connector axis or outer surface thereof may be differently shaped and arranged eccentrically, concentrically or obliquely with respect to spindle connector axis.

EFFECT: reduced costs of spindle usage.

5 dwg

Up!