Driving device for oil and gas well drilling tool

Abstract

The invention relates to the field of oil and gas well drilling tools, and particularly discloses a driving device for an oil and gas well drilling tool, which comprises a turbine section assembly, a speed reduction section assembly and a universal joint assembly which are connected in sequence, and the turbine section assembly is used for guiding and inputting drilling fluid of the oil and gas well drilling tool into the speed reduction section assembly; the high-rotation-speed momentum is input into the speed reduction joint assembly through the guided-in drilling fluid, the speed reduction joint assembly is used for reducing the speed and increasing the torque of the input high-rotation-speed momentum and transmitting the input torque and the drilling fluid into the universal joint assembly, and the universal joint assembly is used for transmitting the input torque and the drilling fluid into a drill bit of an oil and gas well drilling tool. The driving device meets the requirement for large torque output of a drill bit of a drilling tool; and the lubricating effect is strong, so that the service life is long during deep well drilling of high-temperature, high-pressure and corrosive media.

Description

Technical Field

[0001] This invention relates to the field of oil and gas well drilling tools, specifically a drive device for oil and gas well drilling tools. Background Technology

[0002] Deepwater and deep-seated oil and gas drilling, as well as geothermal drilling, face challenges such as high formation temperatures, strong rock abrasiveness, and high plasticity. Traditional rotary drilling methods suffer from significant torque loss and severe wear on drill pipes and casing, resulting in extremely low drilling speeds during development. Current drilling methods often employ both screw drills and turbine drills to improve drilling speed and efficiency. However, screw drills, due to the presence of rubber components, have limited lifespan under conditions such as high temperatures and oil-based drilling fluids. This is especially true in ultra-deep (≥9000m) formation drilling, geothermal drilling, and ultra-high-temperature drilling, where rubber aging makes it difficult to guarantee normal development. Correspondingly, turbine drills, as a type of downhole power drill with all-metal components, have advantages such as high coaxiality, low lateral vibration, small change in working efficiency over time, less stagnation, and insensitivity to oil-based drilling fluids. Furthermore, because all their components are made of metal, they have outstanding wear resistance and high-temperature resistance, are insensitive to various drilling fluids, and have good stability. As a result, they have unparalleled advantages over other traditional downhole drilling tools such as screw drills in adapting to complex drilling environments in deep water and deep formations.

[0003] Currently, mature turbine drilling tools used both domestically and internationally are mainly from foreign companies such as Neyrfor, VN II BT-DrillingTools, and Haliburton Speery. Functionally, they are mainly divided into two types: with and without a reducer. Turbine drilling tools without a reducer often have speeds exceeding 1000 r / min, but correspondingly lower output torque, making them less suitable for the harsh conditions of modern drilling projects and limiting their application range. Turbine drilling tools with reducers generally use planetary gear reducers, which have complex structures. Due to limitations in overall machine size and structure, the reduction ratio of a single reducer is small, and the transmission efficiency, transmission accuracy, and operational stability of multiple reducers are difficult to guarantee. Furthermore, sealing is difficult to ensure in high-temperature, high-pressure, and corrosive environments, making them prone to premature failure. In addition, only Russia's VN II BT possesses commercially successful planetary gear reducers internationally; related technologies in China are not yet mature, and field application conditions still need improvement. Therefore, the application of turbine drills in high-temperature well drilling is still limited, and there is an urgent need to develop new deceleration devices that meet the requirements of high reduction ratio, stable performance, and corrosion resistance, so as to solve the problem of high torque output of turbine drills in high-temperature environments. Summary of the Invention

[0004] In response to the above issues, this invention proposes a drive device for oil and gas well drilling tools that meets the requirements for high torque output of the drill bit; it also has strong lubrication properties, resulting in a long service life during deep well drilling in high-temperature, high-pressure, and corrosive media.

[0005] The objective of this invention can be achieved through the following technical solutions:

[0006] A drive device for oil and gas well drilling tools includes a turbine joint assembly, a reduction joint assembly, and a universal joint assembly connected in sequence. The turbine joint assembly is used to introduce drilling fluid into the oil and gas well drilling tool and input it into the reduction joint assembly, and to input high-speed momentum into the reduction joint assembly through the introduced drilling fluid. The reduction joint assembly is used to decelerate and increase torque of the input high-speed momentum, and to transmit the input torque and drilling fluid into the universal joint assembly. The universal joint assembly is used to transmit the input torque and drilling fluid into the drill bit of the oil and gas well drilling tool.

[0007] In a further embodiment, the turbine joint assembly includes a turbine joint housing, an upper adjusting sleeve, a locking cap, a drive structure, a turbine joint mandrel, and a rotary dynamic seal. The upper adjusting sleeve is disposed inside the turbine joint housing. The drive structure is connected inside the turbine joint housing, and one end is drivenly connected to the turbine joint mandrel. The locking cap is connected to the other end of the drive structure. A second flow channel for drilling fluid input is provided between the upper adjusting sleeve and the locking cap. The rotary dynamic seal is sealed between the turbine joint mandrel and the turbine joint housing to prevent drilling fluid from flowing out of the turbine joint housing from the turbine joint mandrel.

[0008] In a further embodiment, the drive structure includes a radial bearing outer ring, a turbine joint stator and rotor, and a radial bearing inner ring. The turbine joint stator and rotor are connected to the middle of the turbine joint housing. The radial bearing outer ring and the radial bearing inner ring are rotatably connected to each other. The rotor of the turbine joint stator and rotor is rotatably connected to the turbine joint housing via the radial bearing outer ring and the radial bearing inner ring. The rotor of the turbine joint stator and rotor is rotatably connected to the stator, and the stator is connected to the turbine joint housing. A locking cap is connected to one end of the rotor of the turbine joint stator and rotor to press the radial bearing inner ring from the end. A fifth flow channel is provided inside the radial bearing outer ring for inputting drilling fluid from the second flow channel to the turbine joint stator and rotor. The turbine joint core... The shaft is connected to the other end of the rotor of the turbine section stator and rotor. A third flow channel is provided between the turbine section mandrel and the turbine section housing. The third flow channel is used to input drilling fluid flowing from the turbine section stator and rotor. A fourth flow channel is evenly distributed on the inner circumference of the turbine section mandrel and is arranged obliquely. The fourth flow channel is connected to the third flow channel. An eccentric hole is provided at the end of the turbine section mandrel away from the turbine section stator and rotor. The eccentric hole is connected to the fourth flow channel. The stator blades and rotor blades of the turbine section stator and rotor include multiple sets. The multiple sets of stator blades and rotor blades are separated by the outer ring and inner ring of the radial bearing. The turbine section stator and rotor drive the rotor blades to rotate in the opposite direction by the drilling fluid flowing through the stator blades.

[0009] In a further embodiment, the reduction gear assembly includes a reduction gear stator and a reduction gear rotor. The reduction gear stator is connected to the turbine joint housing. The shaft end of the reduction gear rotor is inserted into the eccentric hole. The reduction gear rotor and the reduction gear stator form a transmission pair through helical internal meshing. The eccentricity of the eccentric hole is consistent with the eccentricity of the reduction gear rotor relative to the stator, and the pitch is the same. The stator lead Ts and the rotor lead T form a proportional relationship: T / T s =N / (N+1), where N represents the number of rotor heads, and the rotor of the speed reduction section is provided with a sixth flow channel, which is connected to the fourth flow channel;

[0010] A dynamic sealing structure, a tapered roller bearing, and a radial bearing are sequentially connected between the deceleration section rotor and the wall of the eccentric hole. The dynamic sealing structure is used for radial sealing between the deceleration section rotor and the wall of the eccentric hole. The tapered roller bearing is used for axial sliding between the deceleration section rotor and the wall of the eccentric hole. The radial bearing is used for radial sliding between the deceleration section rotor and the wall of the eccentric hole.

[0011] In a further embodiment, an eighth flow channel is provided inside the deceleration section stator, which is connected to the meshing point of the deceleration section stator and the deceleration section rotor. A seventh flow channel and a ninth flow channel are respectively provided between the two ends of the deceleration section stator and the deceleration section rotor. The seventh flow channel, the ninth flow channel, the eighth flow channel, the lubrication cavity of the tapered roller bearing, and the lubrication cavity of the radial bearing are connected.

[0012] In a further embodiment, the universal joint assembly includes a universal joint housing and a universal joint spindle. The universal joint housing is connected to the stator of the reduction gear, and the universal joint spindle is connected to the rotor of the reduction gear. The universal joint spindle is disposed within the universal joint housing. The universal joint housing includes a straight housing structure, a curved housing structure, or a housing structure with adjustable curvature. The universal joint spindle is a universal drive shaft. A tenth flow channel is provided inside the universal joint spindle, and the tenth flow channel communicates with the sixth flow channel.

[0013] In a further embodiment, an eleventh flow channel is provided between the universal joint housing and the universal joint spindle. The eleventh flow channel is connected to the ninth flow channel, and a piston sliding seal structure for channel sealing is provided on the eleventh flow channel. The piston sliding seal structure can be slidably connected within the eleventh flow channel.

[0014] In a further embodiment, the universal joint assembly is connected to a lower connecting structure at the end away from the reduction joint assembly. The lower connecting structure is used to transmit the torque and drilling fluid input from the universal joint assembly to the drill bit of the oil and gas well drilling tool, and to reduce wear on both during transmission. The turbine joint assembly is connected to an upper connecting structure at the end away from the reduction joint assembly for connecting with the drill string of the oil and gas well drilling tool, and for transmitting drilling fluid from the drill string to the turbine joint assembly.

[0015] In a further embodiment, the lower connecting structure includes a lower connecting housing and a lower connecting mandrel. The lower connecting housing is connected to the universal joint housing, and the lower connecting mandrel is connected to the universal joint mandrel. The lower connecting mandrel is connected inside the lower connecting housing, and a twelfth flow channel is provided inside the lower connecting mandrel, which communicates with the tenth flow channel. The upper connecting structure includes an upper connecting housing, which is connected to the turbine joint housing. A first flow channel is provided inside the upper connecting housing, and the first flow channel communicates with the second flow channel.

[0016] In a further embodiment, the lower connecting housing and the lower connecting spindle are connected sequentially by an upper radial bearing assembly, a thrust bearing assembly, an anti-detachment structure, and a lower radial bearing assembly. The anti-detachment structure is used to prevent the thrust bearing assembly from sliding off axially. A pressure relief hole is provided at one end of the universal joint housing near the lower connecting housing. The pressure relief hole is used to relieve pressure at the eleventh flow channel.

[0017] The beneficial effects of this invention are:

[0018] The drive device of this invention, through the coordinated action of the turbine joint assembly, the reduction joint assembly, and the universal joint assembly, can achieve high torque output, enabling both vertical well operations and directional drilling operations.

[0019] This invention achieves this by aligning the eccentricity of the turbine mandrel's eccentric hole with the eccentricity of the reduction gear rotor relative to the stator. This converts the fixed-axis motion of the turbine mandrel into the circular motion of the reduction gear rotor, ensuring that the reduction gear rotor's revolution speed equals the turbine mandrel's rotation speed. After the reduction gear rotor's coordinated motion, this is converted into the reduction gear rotor's rotation speed. For an N-head rotor, the reduction ratio can achieve an N:1 effect. The ratio of the number of stator heads to rotor heads can be determined based on the turbine mandrel's output speed and the required drilling torque. This effectively converts hydraulic energy into the inertial mechanical energy of the reduction gear rotor.

[0020] The working medium of the deceleration unit stator and rotor is grease or oil lubricant, and the lubrication points are isolated from the external mud system by a sealed lubrication structure and a piston sliding seal structure. The grease-containing lubricant can ensure low frictional resistance in the meshing transmission parts and improve their service life.

[0021] The piston sliding seal structure at the lower end of the universal joint spindle in the universal joint assembly achieves lower lubrication and sealing of the reduction joint assembly. Through the pressure relief hole, the pressure can be connected with the outer annulus to achieve pressure balance. Attached Figure Description

[0022] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0023] Figure 1 This is a schematic diagram of the drive unit structure;

[0024] Figure 2 This is a schematic diagram showing the structure and connection of the turbine assembly and its sealing and lubrication structure.

[0025] Figure 3 This is a schematic diagram of the radial bearing structure of the turbine section;

[0026] Figure 4 The stator and rotor structure and working principle diagram of the turbine section;

[0027] Figure 5 This is a schematic diagram showing the connection between the sealing and lubrication structure and one end of the speed reduction rotor.

[0028] Figure 6 This is a right-end view of the turbine mandrel;

[0029] Figure 7 This is a schematic diagram of the speed reduction joint assembly.

[0030] Figure 8 A schematic diagram of the stator and rotor configuration for a reduction gear with N / N+1 heads;

[0031] Figure 9 This is a structural schematic diagram of the universal joint assembly;

[0032] Figure 10 This is a schematic diagram of the bend in the universal joint housing.

[0033] Figure 11 This is a structural diagram of the lower connection structure;

[0034] Figure 12 This is a schematic diagram of a PDC thrust bearing structure;

[0035] Figure 13 This is a schematic diagram of the lubrication and sealing structure at the speed reduction joint assembly.

[0036] In the diagram: 10 - Upper connecting structure; 20 - Turbine joint assembly; 30 - Sealing and lubrication structure; 40 - Reduction joint assembly; 50 - Universal joint assembly; 60 - Lower connecting structure; 70 - Outlet end; 80 - Inlet end; 21 - Turbine joint housing; 22 - Upper adjusting sleeve; 23 - Locking cap; 24 - Radial bearing outer ring; 25 - Turbine joint stator and rotor; 26 - Radial bearing inner ring; 27 - Turbine joint mandrel; 28 - Dynamic seal structure; 31 - Radial bearing; 32 - Tapered roller bearing; 33 - Rotary dynamic seal; 41 - Reduction joint stator; 42 - Reduction joint rotor; 51 - Universal joint housing ; 52-Universal joint mandrel; 53-Piston sliding seal structure; 61-Lower connecting housing; 62-Lower connecting mandrel; 63-Upper radial bearing assembly; 64-Thrust bearing assembly; 65-Anti-detachment structure; 66-Lower radial bearing assembly; 100, 210, 220, 230, 241, 400, 420, 430, 440, 500, 510, 600-First to twelfth flow channels for drilling fluid or lubricating oil respectively; 200, 240, 410, 450, 460, 610, 620-First to seventh tapered threads for upper and lower connection; 520-Pressure relief hole. Detailed Implementation

[0037] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0038] Figure 1 This is a schematic diagram of the overall structure of the invention. It mainly consists of six parts: an upper connecting structure 10, a turbine joint assembly 20, a sealing and lubrication structure 30, a reduction joint assembly 40, a universal joint assembly 50, and a lower connecting structure 60. When this drive device for oil and gas well drilling tools is in operation, it is connected as a whole to the combined drill string. The upper connecting structure 10 can be connected to the drill string through the inlet end 80, and the lower end 70 of the lower connecting structure 60 can be connected to the drill bit through threads. During operation, drilling fluid flows in through the first flow channel 100, then through the fifth flow channel 241, and then through the stator and rotor of the turbine joint assembly 20. It then flows through the fourth flow channel 230 of the stator at the lower end of the turbine joint assembly 20 to the sixth flow channel 400 of the reduction joint rotor 42 of the reduction joint assembly 40, and then through the internal channels of the universal joint assembly 50 and the lower connecting structure 60 to the outlet end 70, finally flowing through the drill bit to the bottom of the well, achieving flushing of the well bottom.

[0039] The upper connecting structure 10 can include two structures: one is a short section that only serves as a connection to the main drill string; the other is a bypass valve structure with a bypass function. In ultra-deep drilling (>5000 meters), the following is adopted... Figure 1 The structural form is as follows: When drilling at shallower depths, a bypass valve structure with a bypass function is used. This allows the drilling fluid that may be carried out during tripping out of the wellhead to be discharged into the annulus through the bypass structure, preventing the drilling fluid from being carried to the wellhead when the drill pipe is pulled out. This bypass valve technology is relatively mature and widely used. The upper connection structure 10 can also be integrated into the drill string or turbine assembly.

[0040] Figure 2 This is a schematic diagram of the turbine joint assembly structure and the sealing and lubrication structure 30. The turbine joint assembly 20 can be composed of a turbine joint housing 21, an upper adjusting sleeve 22, a locking cap 23, a radial bearing outer ring 24, a turbine joint stator and rotor 25, a radial bearing inner ring 26, a turbine joint spindle 27, and a dynamic sealing structure 28.

[0041] The first tapered thread 200 of the turbine section housing 21 is connected to the upper connector assembly 10 via a tapered thread, and the lower interface of the turbine section housing 21 is connected to the reduction section stator 41 of the reduction section assembly 40 via a second tapered thread 240.

[0042] The aforementioned locking cap 23 and turbine joint spindle 27 are threaded together to press the radial bearing moving ring 26 of the turbine joint assembly 20 and the rotor in the turbine joint stator 25, so that the three of them have the same direction of operation.

[0043] The outer ring 24 of the radial bearing is pressed together by the upper adjusting sleeve 22 and the turbine section housing 21 under the engagement of the lower thread of the upper joint assembly 10, so that they have a common direction of operation.

[0044] Figure 3 This is a schematic diagram of the outer ring 24 of the radial bearing. Those skilled in the art will recognize that the outer ring 24 and the inner ring 26 of the radial bearing can roll relative to each other, serving to bear lateral forces while converting friction between them into rolling friction, thus ensuring relative rotation between the turbine segment housing 21 and the turbine segment spindle 27. Simultaneously, the outer ring 24 of the radial bearing has five circumferentially distributed flow channels 241 for downward transmission of drilling fluid.

[0045] The lower end of the turbine joint mandrel 27 contains three circumferentially distributed fourth flow channels 230, but not limited to three, with an inclination angle of 30°, but not limited to 30°. When drilling fluid flows through the first tapered thread 200, it first passes through the second flow channel 210, and then flows through the fifth flow channel 241 of the radial bearing outer ring 24 to the turbine joint stator and rotor 25, driving the rotor to rotate. Then the drilling fluid flows out from the rotor 25 and is guided through the fourth flow channels 230 at the lower part of the turbine joint mandrel 27.

[0046] Figure 4 This diagram illustrates the structure and working principle of the turbine joint stator and rotor 25. The turbine joint stator and rotor 25 employs an inverted stator and rotor blade structure. In conventional turbine drill bits, the stator blades remain fixed relative to the outer casing during operation, acting as a guide to direct the working medium towards the rotor blades. This drives the rotor blades and turbine joint spindle 27 to rotate clockwise at high speed, converting hydraulic energy into the kinetic energy of the turbine joint spindle 27. Similarly, the turbine joint 25 of this invention still consists of stator and rotor blades (temporarily referred to as a reverse-rotation turbine joint). The difference is that the structural angle (or installation angle) of the stator blades is opposite to that of conventional turbine joint stator blades. Through the guiding effect of the stator blades, the fluid drives the rotor blades to rotate counterclockwise, thus outputting high-speed counterclockwise rotation.

[0047] Figure 5This is a schematic diagram showing the connection between the sealing and lubrication structure 30 and one end of the reduction gear rotor 42. The sealing and lubrication structure 30 at this end may include a rotary dynamic seal 33, a tapered roller bearing 32, and a radial bearing 31 arranged sequentially. The tapered roller bearing 32 is used to withstand axial hydraulic loads and radial vibration and centrifugal forces. The upper end of the tapered roller bearing 32 contacts the turbine shaft 27, and the lower end of the tapered roller bearing 32 contacts the reduction gear assembly rotor 42. The tapered roller bearing ensures rolling friction between the two rotors during relative motion. The sealing position and requirements of the sealing sliding structure can be adapted and selected as needed. The number and type of bearings or seals can be selected or matched with existing seal and bearing structures.

[0048] The turbine section spindle 27 bears a downward hydraulic load under the action of fluid. This load is transmitted downward through the tapered roller bearing and the reduction section rotor 42 of the reduction section assembly 40, and is ultimately offset by the drilling pressure from the bottom of the well.

[0049] The turbine joint spindle 27 and the turbine joint housing 21 form a rotary dynamic seal. The rotary dynamic seal 28 can be a lip seal or other types of seals, and there can be one set or multiple sets. The function of the seal is to ensure that the drilling fluid in the third flow passage 220 can only flow through the fourth flow passage 230 to the internal sixth flow passage 400 of the reduction joint rotor 42.

[0050] The rotary dynamic seal 33 employs a lip-shaped or other dynamic seal structure to ensure that drilling fluid flowing through the 400-hole channel cannot enter the interior of the tapered roller bearing 32, thereby ensuring the long-term operation of the tapered roller bearing 32.

[0051] The radial bearing 31 serves to straighten and ensure relative rolling between the turbine joint spindle 27 and the reduction joint rotor 42. Its lubricating medium is grease or liquid oil, which is used to ensure rolling friction between components, reduce rolling friction force, and increase normal working time.

[0052] Figure 6 This is a right-end view of the turbine mandrel 27. The hole at the bottom of the turbine mandrel 27 that mates with the reduction gear assembly 40 is an eccentric hole structure with an eccentricity of e, which is the same as the eccentricity value of the reduction gear rotor relative to the stator. This ensures that when the turbine mandrel 27 rotates on its fixed axis, the reduction gear assembly 40 can maintain a circular motion with the eccentricity e as the radius and the center of the reduction gear stator as the center.

[0053] Figure 7 This is a schematic diagram of the reduction gear assembly 40. The all-metal motor reduction gear assembly 40 mainly consists of two parts: a stator 41 and a reduction gear rotor 42. All components of the motor are made of metal, which facilitates maintaining a long service life in high-temperature environments.

[0054] The upper end of the reduction gear assembly 40 is connected to the turbine assembly 20, and the lower end is connected to the universal joint assembly 50. The upper end of the reduction gear stator 41 is connected to the turbine housing 21 via a third tapered thread 410, and the lower end is connected to the universal joint housing 51 of the universal joint assembly 50 via a fourth tapered thread 450. The upper end of the reduction gear rotor 42 is inserted into the eccentric hole at the lower end of the turbine mandrel 27 of the turbine assembly 20, and the lower end is connected to the mandrel 52 of the universal joint assembly 50 via a fifth tapered thread 460.

[0055] The reduction gear assembly consists of a reduction gear stator and a reduction gear rotor that mesh helically with the same pitch but different leads. The stator lead Ts and the rotor lead T are proportional, forming a helical transmission pair. Assuming the rotor has N heads, the stator has N+1 heads, ensuring that the stator has one more helical head than the rotor, with N ≥ 1.

[0056] T / T s =N / (N+1)

[0057] The reduction gear stator and reduction gear rotor of the reduction gear assembly are fitted with a clearance fit, with a clearance value of not less than 0.2 mm and not more than 1.5 mm, and the working medium between the stator and rotor is a grease-based lubricant. The clearance value and the presence of the lubricating medium ensure that the friction between the stator and reduction gear rotor is reduced during relative motion, thus ensuring a longer service life.

[0058] The stator and rotor surfaces of the reduction gear assembly undergo surface strengthening treatment. This treatment can be achieved through surface spraying of a wear-resistant coating or processes such as carburizing and nitriding, and is not limited to these specific surface strengthening techniques. The treated surface exhibits improved wear resistance and hardness compared to the original surface, with an improvement of at least 10%.

[0059] The length of the stator-rotor mating surface of the reduction gear assembly is 0.5-1.5 times the stator helix lead, preferably less than 1 lead, to ensure that the meshing pair is unlikely to form a top-to-bottom seal transmission, thus avoiding excessive downward pumping pressure on the lubricating medium. Secondly, its shorter structural dimensions result in a compact structure, saving space in the drive unit.

[0060] Figure 8 This is a schematic diagram of the stator and rotor assembly of a reduction gear with N / N+1 heads. The reduction gear stator 41 has evenly distributed eighth flow channels 430 circumferentially. The dimensions of the eighth flow channels 430 must not affect the strength requirements of the reduction gear stator during normal operation. The hollow sixth flow channel 400 in the reduction gear rotor 42 is used for the flow of drilling fluid from top to bottom through the tool.

[0061] Grease-based lubricating media are present in the evenly distributed eighth flow channel 430 of the reduction gear stator and in the relative gaps between the reduction gear stator 41 and the reduction gear rotor 42. A ninth flow channel 440 for grease flow can be provided locally on the circumference of the reduction gear stator to facilitate the mutual flow of the internal lubricating media, thereby ensuring continuous lubrication. When the reduction gear stator and rotor rotate relative to each other, the lubricating media can circulate through the ninth flow channel 440 in the gap between the stator and rotor and in the eighth flow channel 430 of the stator, thus ensuring sufficient grease lubrication between the all-metal mating surfaces of the stator and rotor, further reducing metal-to-metal friction.

[0062] The relative motion of the stator and rotor in the reduction gear section is similar to that of a planetary gear reduction structure. When the stator 41 of the reduction gear section remains stationary, the rotor rotates at its own speed n. 自 Revolutionary speed n 公 Planetary motion occurs within the stator housing, and the ratio of its rotation to revolution is shown in the following formula. The negative sign indicates that the rotation and revolution are in opposite directions, and N is the number of rotor heads. Therefore, when the turbine assembly 20 transmits high-speed rotation to the reduction rotor 42 of the reduction assembly 40 via the turbine mandrel 27 and eccentric hole, it is equivalent to converting the fixed-axis rotation of the turbine mandrel 27 into the revolution motion of the reduction rotor 42. After conversion of the rotational speed of the stator and rotor, a 1 / N multiple speed output is achieved. The rotational speed of the reduction rotor is extracted by the universal joint assembly structure 50 and transmitted to the drill bit to achieve the deceleration function. Similarly, according to the principle of energy conservation, input power equals output power. Under the same power, higher speed results in lower torque, and lower speed results in higher torque. Therefore, the torque increases accordingly after converting from high speed to low speed.

[0063]

[0064] P = n 入 T 入 =n 出 T 出

[0065] n 入 =n 公

[0066] n 出 =n 自

[0067]

[0068] Figure 9This is a schematic diagram of the universal joint assembly 50. The universal joint assembly 50 mainly consists of a universal joint housing 51, a universal joint spindle 52, and a piston sliding seal structure 53. Its function is to convert the high-speed fixed-axis rotation of the turbine joint assembly 20 into the revolution and rotation of the rotor reduction joint 42 after passing through the reduction joint assembly 40. The revolution speed is the same as the output speed of the turbine joint rotor, while the rotation speed is 1 / N of the revolution speed. The universal joint assembly 50 extracts the rotation of the reduction joint rotor 42 through the conversion of the universal joint spindle 52 and transmits the rotation speed downward to the lower connecting structure 60, and then to the drill bit.

[0069] Figure 10 This is a schematic diagram of the bend in the universal joint housing. The universal joint housing 51 in the universal joint assembly 50 has two functions: one is a straight housing structure, enabling drilling in vertical or steadily inclined well sections; the other is a bend in the housing, enabling directional drilling in a specific direction, or combined drilling at small bends (<1.5°). The housing 51 with a certain bend angle (0°-3°) has various structural forms:

[0070] like Figure 10 As shown in Figures b and d, the single-bend form - the outer shell is a one-time bending structure. The bending point can be set at the upper or lower part of the outer shell. For the same angle, the offset distance of the lower bending point is smaller, and the achievable slope ratio is relatively higher.

[0071] like Figure 10 The double-bend structure shown in Figures a and c has two coplanar bends in two directions on the outer shell, which can be coplanar in the same direction or coplanar in opposite directions. Double-bend structures are characterized by large bend angles, small offset distances, and high slope.

[0072] Adjustable bend type - The bend angle of the outer shell is adjustable. The bend angle can be adjusted on-site according to the required inclination rate. The adjustment range is 0°-3°. The bend angle can be adjusted both on the ground and downhole.

[0073] The universal joint assembly spindle 52 can be either a flexible shaft or a combination of movable joints. It is not limited to ball joints, ten-joint joints, etc. That is, the universal joint structure that can be used on positive displacement motor screw drills can also be used in this invention.

[0074] Figure 11This is a schematic diagram of the lower connecting structure 60. The lower connecting structure mainly consists of six parts: a lower connecting housing 61, a lower connecting mandrel 62, an upper radial bearing assembly 63, a thrust bearing assembly 64, an anti-detachment structure 65, and a lower radial bearing assembly 66. The function of the lower connecting structure is to transmit the rotation of the mandrel 52 from the universal joint to the drill bit, while simultaneously bearing radial vibrations and axial drilling pressure through its radial and thrust bearings.

[0075] The lower connecting structure 60 has a lower connecting housing 61 connected to the outer housing 51 of the universal joint assembly 50 via a sixth tapered thread 610. The internal turbine joint spindle 62 is connected to the lower end of the universal joint spindle 52 in the universal joint assembly 50 via a straight thread and a screw, thereby enabling the transmission of rotational speed and torque to the lower connecting spindle 62 through the thread, and subsequently to the drill bit for rock breaking. The lower end of the lower connecting spindle 62 is connected to the drill bit via a seventh tapered thread 620 to facilitate the transmission of torque and rotational speed.

[0076] The lower connecting structure 60, when the drilling medium flows, flows from the upper tenth flow channel 500 to the lower connecting mandrel 62's internal twelfth flow channel 600, and then from the internal twelfth flow channel 600 to the drill bit, achieving impact rock breaking at the bottom of the well. The internal thrust bearing assembly 64 can adopt a ball thrust bearing assembly mode, or a needle roller, ball bearing, or other structure, with no fewer than 5 assemblies. Alternatively, the thrust bearing assembly can also adopt a PDC thrust bearing structure (see [reference needed]). Figure 12 To achieve a longer service life, the lower connecting structure 60 can be integrally integrated into the drill bit or partially integrated into one end of the universal joint assembly 50. The aforementioned structure for tapered thread connection can also be fixedly connected in other ways, which should also be within the scope of protection or disclosure in this field.

[0077] Figure 13This is a schematic diagram of the lubrication and sealing structure of the reduction gear assembly. The reduction gear assembly has an independent lubrication and sealing system, which mainly consists of a sealing system and a lubrication system. The upper rotary dynamic seal 33 isolates the fluid inside the reduction gear rotor 42 from the lubricating medium, and the lower piston sliding seal structure 53 isolates the external drilling medium from the lubricating medium. The piston sliding seal structure 53 can achieve axial displacement. When the reduction gear stator and rotor of the reduction gear assembly are engaged, the lubricating medium located above the stator (stored in the space of the eleventh flow channel 510) is transferred to the space of the eleventh flow channel 510 through the "pump" action of the screw motor of the reduction gear assembly. At this time, the left end of the piston sliding seal structure 53 contains lubricating medium with a certain pressure, and the right end is connected to the external annulus through the pressure relief hole 520. When the pressure at the left end is relatively high, the piston sliding seal structure 53 moves to the right; when the external pressure is high, the piston sliding seal structure 53 moves to the left, thereby achieving pressure balance between the lubrication sealing cavity and the external environment. Meanwhile, after the lubricating medium is transported to the eleventh flow channel 510 chamber through the "pump" action, the amount of lubricating medium at the left end is relatively small. At this time, the fluid is interconnected through the evenly distributed eighth flow channel 430, thus making the entire reduction mechanism a lubricating environment with a relatively uniform lubricating medium. The structure on the right side of the pressure relief hole 520, which can also be connected to the front end of the deceleration section stator and rotor screw through the flow channel, should also be included in the scope of disclosure or protection of this application.

[0078] In a specific working process, during high-temperature formation drilling, drilling fluid flows in through the first flow channel 100 and then through the second flow channel 210 of the annular star between the locking cap 23 and the upper adjusting sleeve 22 to the stator and rotor of the turbine joint rotor 20. With the cooperation of the stator and rotor, the turbine joint rotor shaft rotates at high speed, converting the pressure energy of the drilling fluid into the output kinetic energy of the turbine joint spindle 27. The rotation of the turbine joint spindle 27 is converted through the eccentric hole 30 into the circular revolution of the reduction joint rotor 42 and its own rotational motion around the reduction joint stator 41. The rotation of the rotor is extracted through the conversion action of the universal joint spindle 52 of the universal joint assembly 50. Since the reduction joint assembly with N-head reduction joint rotor 42 has a revolution-rotation output speed ratio of N:1, the reduction joint assembly 40 achieves a reduction effect. Simultaneously, due to the inverse proportional relationship between speed and torque under constant power, the output torque is amplified to N times, thus achieving the high torque output characteristic of the reduction joint assembly 40. The rotational speed and torque of the reduction joint rotor are transmitted to the drill bit through the universal joint spindle 51 and the lower connecting spindle 62, thereby achieving rock breaking. At the same time, the drilling fluid is also transmitted to the drill bit through various flow channels to achieve flushing.

[0079] The aforementioned speed reduction assembly can preferentially use a metal screw motor speed reduction structure, and can be a simple single-stage structure, or a motor speed reduction structure made of other wear-resistant and high-temperature resistant materials.

[0080] When assembling the whole machine, especially when assembling the turbine joint mandrel and the reduction section rotor, the rotor should be properly inserted into the eccentric hole of the turbine joint mandrel. The collinearity of the axis of the eccentric hole and the center line of the assembled reduction section rotor is the basis for ensuring normal operation.

[0081] The rotor helixes of the reduction section are all right-handed. As the main component of the reduction section, the rotor undergoes planetary motion within the stator. The counterclockwise revolution of the rotor generates its clockwise rotation, which in turn drives the drill bit to break rock and drill. Simultaneously, due to the large output torque, the length of the turbine section can be effectively reduced, shortening the overall structural dimensions of the machine.

[0082] In the description of this specification, references to terms such as "an embodiment," "example," "specific example," etc., indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of the invention. In this specification, illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples.

[0083] The foregoing has shown and described the basic principles, main features, and advantages of the present invention. Those skilled in the art should understand that the present invention is not limited to the above embodiments. The embodiments and descriptions in the specification are merely illustrative of the principles of the invention. Various changes and modifications can be made to the invention without departing from its spirit and scope, and all such changes and modifications fall within the scope of the claimed invention.

Claims

1. A drive apparatus for an oil and gas well drilling tool, characterized by, The turbine joint assembly (20) is used for guiding and inputting the drilling fluid of the oil and gas well drilling tool into the speed reduction joint assembly (40) and inputting high-speed momentum to the speed reduction joint assembly (40) through the guided drilling fluid, the speed reduction joint assembly (40) is used for reducing the speed and increasing the torque of the input high-speed momentum and transmitting the input torque and the drilling fluid into the universal joint assembly (50), and the universal joint assembly (50) is used for transmitting the input torque and the drilling fluid into the drill bit of the oil and gas well drilling tool.

2. A drive apparatus for a well drilling tool according to claim 1, characterized in that The turbine joint assembly (20) comprises a turbine joint shell (21), an upper adjusting sleeve (22), a locking cap (23), a driving structure, a turbine joint spindle (27) and a rotary dynamic seal (28), the upper adjusting sleeve (22) is arranged in the turbine joint shell (21), the driving structure is connected in the turbine joint shell (21) and is drivingly connected with the turbine joint spindle (27) at one end, the locking cap (23) is connected at the other end of the driving structure, a second flow passage (210) for inputting the drilling fluid is arranged between the upper adjusting sleeve (22) and the locking cap (23), and the rotary dynamic seal (28) is sealingly connected between the turbine joint spindle (27) and the turbine joint shell (21) and is used for preventing the drilling fluid from flowing out of the turbine joint spindle (27) to the outside of the turbine joint shell (21).

3. A drive apparatus for a well drilling tool according to claim 2, wherein, The driving structure comprises a radial bearing outer ring (24), a turbine section fixed rotor (25) connected in the middle of a turbine section housing (21), and a radial bearing inner ring (26) which is matched and rotatably connected with the radial bearing outer ring (24), the rotor of the turbine section fixed rotor (25) is rotatably connected in the turbine section housing (21) through the radial bearing outer ring (24) and the radial bearing inner ring (26), the rotor of the turbine section fixed rotor (25) is matched and rotatably connected with the stator, the stator is connected with the turbine section housing (21), the locking cap (23) is connected at one end of the rotor of the turbine section fixed rotor (25) and is used for pressing the radial bearing inner ring (26) from the end, the radial bearing outer ring (24) is internally provided with a fifth flow passage (241) for inputting the drilling fluid input from the second flow passage (210) to the turbine section fixed rotor (25), the turbine section mandrel (27) is connected at the other end of the rotor of the turbine section fixed rotor (25), a third flow passage (220) is arranged between the turbine section mandrel (27) and the turbine section housing (21) and is used for inputting the drilling fluid flowing from the turbine section fixed rotor (25), the turbine section mandrel (27) is uniformly provided with the fourth flow passage (230) which is obliquely arranged on the inner circumference, the fourth flow passage (230) is communicated with the third flow passage (220), the turbine section mandrel (27) is internally provided with an eccentric hole which is distanced from the turbine section fixed rotor (25) and is communicated with the fourth flow passage (230), the stator blades and the rotor blades of the turbine section fixed rotor (25) comprise a plurality of groups, the stator blades and the rotor blades of the plurality of groups are separated by the radial bearing outer ring (24) and the radial bearing inner ring (26), the turbine section fixed rotor (25) is driven to rotate reversely by the drilling fluid flowing through the stator blades to guide the rotor blades.

4. A drive apparatus for a well drilling tool according to claim 3, wherein The reduction gear assembly (40) comprises a reduction gear stator (41) connected with the turbine section housing (21) and a reduction gear rotor (42) with its shaft end inserted into the eccentric hole, the reduction gear rotor (42) and the reduction gear stator (41) are in transmission by helical internal meshing, the eccentric distance of the eccentric hole is consistent with the eccentric distance of the reduction gear rotor relative to the stator, and the helix pitches are the same, the stator lead Ts and the rotor lead T constitute a proportional relationship: T / T s =N / (N+1), wherein N represents the number of rotor heads, the reduction gear rotor (42) is provided with a sixth flow passage (400) in communication with the fourth flow passage (230); The dynamic sealing structure (33), the tapered roller bearing (32) and the radial bearing (31) are sequentially connected between the rotor (42) of the speed reduction section and the hole wall of the eccentric hole, the dynamic sealing structure (33) is used for radially sealing between the rotor (42) of the speed reduction section and the hole wall of the eccentric hole, the tapered roller bearing (32) is used for axially sliding between the rotor (42) of the speed reduction section and the hole wall of the eccentric hole, and the radial bearing (31) is used for radially sliding between the rotor (42) of the speed reduction section and the hole wall of the eccentric hole.

5. A drive apparatus for a well drilling tool according to claim 4, characterized in that The eighth flow passage (430) is arranged in the speed reduction section stator (41) and is communicated with the meshing position of the speed reduction section stator (41) and the speed reduction section rotor (42), the seventh flow passage (420) and the ninth flow passage (440) are respectively arranged between the two end portions of the speed reduction section stator (41) and the speed reduction section rotor (42), the seventh flow passage (420), the ninth flow passage (440), the eighth flow passage (430), the lubricating cavity of the tapered roller bearing (32) and the lubricating cavity of the radial bearing (31) are communicated.

6. The drive apparatus for a well drilling tool according to claim 3, wherein The universal joint assembly (50) includes a universal joint housing (51) connected with the reduction joint stator (41) and a universal joint core shaft (52) connected with the reduction joint rotor (42), the universal joint core shaft (52) is arranged in the universal joint housing (51), the universal joint housing (51) includes a straight housing joint, a curved housing structure or a housing structure with adjustable bending degree, the universal joint core shaft (52) is a universal transmission shaft, the universal joint core shaft (52) is provided with a tenth flow passage (500) therein, and the tenth flow passage (500) is in communication with the sixth flow passage (400).

7. A drive apparatus for a well drilling tool according to claim 6, characterized in that The universal joint housing (51) and the universal joint core shaft (52) are provided with an eleventh flow passage (510) therebetween, the eleventh flow passage (510) is in communication with the ninth flow passage (440), and the eleventh flow passage (510) is provided with a piston sliding sealing structure (53) for passage sealing, and the piston sliding sealing structure (53) is slidably connected in the eleventh flow passage (510).

8. The drive apparatus for a well drilling tool according to claim 6, wherein The universal joint assembly (50) is connected with a lower connecting structure (60) away from one end of the reduction joint assembly (40), the lower connecting structure (60) is used for transmitting the torque and the drilling fluid input from the universal joint assembly (50) to the drill bit of the oil and gas well drilling tool, and is used for reducing the wear of the two during transmission; the turbine joint assembly (20) is connected with an upper connecting structure (10) for being connected with the drill string of the oil and gas well drilling tool away from one end of the reduction joint assembly (40), and is used for transmitting the drilling fluid at the drill string to the turbine joint assembly (20).

9. A drive apparatus for a well drilling tool according to claim 8, characterized in that The lower connecting structure (60) includes a lower connecting housing (61) connected with the universal joint housing (51) and a lower connecting core shaft (62) connected with the universal joint core shaft (52), and the lower connecting core shaft (62) is connected in the lower connecting housing (61), the lower connecting core shaft (62) is provided with a twelfth flow passage (600) therein, and the twelfth flow passage (600) is in communication with the tenth flow passage (500); the upper connecting structure (10) includes an upper connecting housing (11) connected with the turbine joint housing (21), and the upper connecting housing (11) is provided with a first flow passage (100) therein, and the first flow passage (100) is in communication with the second flow passage (210).

10. A drive apparatus for a well drilling tool as defined in claim 9, characterized in that The lower connecting housing (61) and the lower connecting core shaft (62) are sequentially connected through an upper radial bearing group (63), a thrust bearing group (64), an anti-falling structure (65) and a lower radial bearing group (66), the anti-falling structure (65) is used for preventing the axial sliding falling of the thrust bearing group; the universal joint housing (51) is provided with a pressure relief hole (520) at one end close to the lower connecting housing (61), and the pressure relief hole (520) is used for pressure relief at the eleventh flow passage (510).

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