A variable hydraulic oscillator for underground wells

Abstract

The present invention relates to the field of oil and gas well engineering technology, and in particular to a variable hydraulic oscillator for use downhole, comprising a cylindrical tube body and a plurality of movable turntables arranged at equal intervals along the axial direction of the cylindrical tube body, the inner wall of the cylindrical tube body being provided with a plurality of slots, the movable turntable being rotatably engaged with the plurality of slots via circumferentially arranged bosses, the movable turntable comprising a wheel-shaped structure consisting of a hub, a rim, and a plurality of spokes, the plurality of spokes being arranged between the hub and the rim, the spokes being arranged at an angle, and the inclination angle being adjustable under the action of the fluid. The present invention efficiently converts the kinetic energy of the fluid into the centrifugal mechanical vibration energy of the turntable, achieving radial vibration without the need for external power supply; the inclination angle of the spokes changes with the kinetic energy of the fluid, controlling the radial amplitude, avoiding excessive vibration amplitude affecting the structural stability, and achieving automatic stable adjustment; the larger kinetic energy of the fluid and the rotational mechanical energy are converted into storable electrical energy, thereby improving the stability effect.

Description

Technical Field

[0001] The present invention relates to the technical field of oil and gas well engineering, and in particular to a variable hydraulic oscillator used downhole. Background Art

[0002] During drilling operations, drill string vibration is often required to reduce drilling resistance. Vibration is also often used to overcome resistance in casing installation and assist in cleaning the wellbore. Vibration can also effectively improve cement slurry cementing quality. However, whether drilling vertical, directional, or horizontal wells, the additional torque and friction caused by friction between the drill string and the wellbore can lead to low ROP, difficulty in tool face control, and limited single-pass drilling footage. Friction between the drill string and the wellbore during drilling is a significant factor affecting ROP, necessitating drill string vibration to reduce drilling resistance. Practice has shown that using hydraulic pulses to generate axial oscillations in the drill string can effectively reduce friction between the sliding drill string assembly and the wellbore wall and improve WOB transmission.

[0003] Currently, the main methods for generating radial vibration using hydraulic power include the turbine-driven eccentric method and the screw motor method. However, due to the limited space and diameter of the pipe, achieving the ideal frequency and impact momentum for radial vibration in existing hydraulic downhole vibration tools is more difficult than for axial vibration. Although the turbine-driven eccentric method is simple and easy to implement, it suffers from high hydraulic pressure drop, mechanical friction and eddy current losses, easy clogging of gaps between rotating components, limited vibration impact momentum, and the inability to ensure synchronization when combining multiple stages. The screw motor method, on the other hand, offers advantages such as high efficiency and large radial impact momentum, but is difficult to manufacture and expensive. Summary of the Invention

[0004] In order to solve the above technical problems, the present invention provides a variable hydraulic oscillator for use downhole.

[0005] In order to achieve the above object, the technical solution adopted by the present invention is as follows:

[0006] The wheel hub is annularly fixed to the chassis, and the wheel hub has an angular channel formed between the cam and the hub, and the channel is connected to the axis of the wheel hub to form a circular arc. The wheel hub has a circle which is parallel to the axis of the wheel hub and the axis of the hub. The circular arc has a circle which is parallel to the axis of the wheel hub and the axis of the hub. The circular arc has a circle which is parallel to the axis of the wheel hub and the axis of the hub. The circular arc has a circle which is parallel to the axis of the wheel hub and the axis of the hub.

[0007] Furthermore, the side wall of the hub is provided with a snap-in groove corresponding to the number of spokes, and the snap-in groove is inclined along the axial direction of the hub, and the socket is provided in the middle of the upper end of the snap-in groove. The axial inclination angle of the snap-in groove is 15°, which matches the incident angle of the vortex fluid. When the spokes rotate, the combined force direction of the fluid impact force and the centrifugal force is parallel to the inclined surface of the snap-in groove, thereby maximizing the conversion of the liquid flow energy into the rotational potential energy of the spokes. The socket is located in the middle of the upper end of the snap-in groove, forming a fulcrum for the rotation of the spokes. At low flow rates, the fluid driving force is amplified through the lever effect, thereby improving the initial starting torque. At high flow rates, a larger flow volume is released through the rotation of the spokes, ensuring that the spokes can stably trigger radial vibration under different flow rates.

[0008] Furthermore, the lower width of the engaging groove is greater than that of the spokes, and when the torsion spring is unstressed, the spokes contact the upper surface of the inclined surface of the engaging groove. The gradually expanding engaging groove design forms a fluid dynamics adaptive adjustment channel. When the fluid kinetic energy increases and the hydraulic torque exceeds the minimum driving force threshold of the torsion spring, the spokes slide toward the groove bottom under the impact of the fluid flow, and the tilt angle automatically increases. At this time, the flow cross-sectional area increases, the torsion spring compression increases, and the spoke displacement triggers negative feedback regulation of the vibration amplitude, achieving vibration momentum fluctuations.

[0009] Furthermore, the cross-sections of the boss and the slot are both T-shaped, and the boss and the slot are movably engaged. This nested fit ensures that when the movable turntable rotates within a limited range, it does not undergo relative displacement with the cylindrical tube. The dovetail-type contact surface effectively disperses radial loads and avoids localized stress concentration. When fluid flows through the inclined spokes, the movable turntable can rotate freely, thereby achieving radial vibration.

[0010] Furthermore, a counterweight is provided at the bottom of the rim, and the counterweight does not contact the inner wall of the cylindrical tube. The asymmetric counterweight design generates a controllable centrifugal force field through mass eccentricity. When the rotating speed of the movable turntable reaches a critical value, the centrifugal force of the counterweight produces a vector superposition at a specific phase angle, which can increase the radial vibration momentum and ensure the continuity of the vibration waveform and the energy transfer efficiency. The spoke directions and angles of the movable turntables at each level are the same. In a multi-stage shaft turntable group, the movable turntable of the upper level can guide the movable turntable of the lower level, thereby accelerating the rotation of the vortex of the lower level. The fluid movement between adjacent levels of the multi-stage structure will affect each other, and the offset of the cylindrical tube body caused by the vibration will also cause mutual influence between the levels.

[0011] Furthermore, the three movable turntables are provided, and the length of the counterweight is no greater than the distance between any two of them. During rotation, the counterweight does not interfere with the rotation of the lower movable turntable. The staggered arrangement of the three-stage turntable creates a resonance enhancement effect, which, combined with the counterweight, allows for energy superposition within a vibration frequency range of 100-500Hz.

[0012] Furthermore, an annular thread structure is provided on the top inner side wall of the rim, and a bevel gear rod extending toward the multi-stage shaft-type turntable assembly is provided on the upper end of the columnar tube body, and the bevel gear end of the bevel gear rod is movably abutted and meshed with the annular thread structure. During the meshing process, the transmission damping generated by the bevel gear pair directly acts on the rim of the movable turntable, realizing the three-stage adjustment of "strong vibration-stable vibration-suppression vibration". The matching of the helix angle of the annular thread structure and the bevel gear tooth profile can reduce the meshing impact and improve the transmission efficiency. At the same time, the axial force component of the thread structure is transmitted to the power generation module through the bevel gear rod, forming an axial preload compensation mechanism to avoid the risk of gear disengagement under high vibration conditions. When the power generation module is started, the magnetic coupling between the rotating teeth and the rotor generates a reverse electromagnetic torque, which is transmitted in reverse to the movable turntable through the bevel gear pair, forming a closed-loop control of the speed.

[0013] Furthermore, the control end of the bevel gear rod is connected to a drive control module, which controls the axial movement of the bevel gear rod along the cylindrical tube. The drive control module houses a micro-hydraulic servo mechanism that dynamically adjusts the axial vibration of the bevel gear rod by real-time monitoring of the fluid pressure and vibration acceleration within the cylindrical tube 1. When the flow rate exceeds a set threshold, the module drives the bevel gear rod toward the annular thread structure, causing the bevel gear to engage with the annular thread structure. At this point, the system converts rotational mechanical energy into electrical energy. Simultaneously, the gear pair's transmission damping effect reduces the speed of the movable turntable, achieving amplitude attenuation. Closed-loop control ensures stable vibration momentum.

[0014] Furthermore, a power generation module is provided at one end of the drive control module. Coaxially disposed teeth are provided on the bevel gear rod, and a rotor that cooperates with the teeth is provided on the power generation module. The power generation module adopts a magnetically coupled power generation system, i.e., a non-contact design of a permanent magnet array and a stator winding. When the bevel gear rod is engaged with the annular thread structure, the rotation of the movable turntable drives the bevel gear rod to rotate at a set reduction ratio through the annular thread structure, driving the teeth to cut the magnetic flux lines at a set speed, generating direct current and storing it in a high-temperature resistant lithium battery pack. This process simultaneously generates a reverse electromagnetic torque, which reduces the driving torque of the movable turntable, forming a negative feedback regulation of the speed, thereby suppressing overload vibration.

[0015] Furthermore, when the bevel gear end engages with the annular threaded structure, the rotating teeth mesh with the rotor, thereby converting the mechanical energy generated by the hydraulically driven rotation of the multi-stage shaft-type turntable assembly into storable electrical energy. The multiple movable turntables are fixedly connected by a central axis. When the movable turntables are fixedly connected by the central axis, the counterweights on each movable turntable are aligned vertically, ensuring that the same centrifugal force is generated during rotation. The synchronous transmission of torque across the three turntables enhances energy conversion and avoids the high energy losses and insufficient energy conversion associated with single-stage energy transmission.

[0016] Compared with the prior art, the present invention has the following beneficial effects:

[0017] 1. The present invention features inclined spokes that, through coupling with swirling hydraulics, efficiently convert fluid kinetic energy into centrifugal mechanical vibration energy for the turntable. Combined with the axial arrangement of the multi-stage rotating shaft turntable assembly, this achieves a cascade amplification effect of energy transfer. The directional superposition of the centrifugal force of the counterweight significantly enhances radial vibration momentum, achieving radial vibration without the need for external power supply and avoiding internal energy consumption caused by phase asynchrony in the multi-stage vibrators.

[0018] 2. The present invention provides rotatable spokes. When the fluid kinetic energy is low, the spokes have a small vertical inclination angle, which increases the rotation speed of the movable turntable and the radial vibration. When the fluid kinetic energy increases, the spokes impact the spokes to increase the vertical inclination, increase the flow rate, reduce the rotation speed of the movable turntable, control the radial vibration, avoid excessive vibration amplitude affecting the structural stability, and achieve automatic stable adjustment.

[0019] 3. The present invention can convert larger fluid kinetic energy and rotational mechanical energy into storable electrical energy by setting up a power generation module. During the conversion process, the rotation speed of the movable turntable can be reduced, thereby improving the stability effect. Compared with the existing technology, the present invention has a simple structure and low cost, can achieve the axial oscillation vibration frequency required by the drill string, and has low pressure loss. It is an economical and effective method for generating radial vibration in oil wells. BRIEF DESCRIPTION OF THE DRAWINGS

[0020] Figure 1 It is a structural cross-sectional view of the present invention;

[0021] Figure 2 It is a schematic diagram of the split structure of the present invention;

[0022] Figure 3 It is a structural diagram of a movable turntable;

[0023] Figure 4 It is a schematic diagram of the split structure of the movable turntable;

[0024] Figure 5 It is a schematic diagram of the split structure of the hub and spokes;

[0025] Figure 6 2. It is a schematic diagram of an application of a bevel gear rod according to an embodiment of the present invention;

[0026] Figure identification: 1-cylindrical tube, 2-movable turntable, 201-hub, 202-rim, 203-spoke, 3-slot, 4-boss, 5-rotating shaft, 6-jack, 7-torsion spring, 8-clamping groove, 9-counterweight, 10-annular thread structure, 11-bevel gear rod, 12-rotating teeth, 13-center axis. DETAILED DESCRIPTION

[0027] In order to make the objectives, technical solutions and advantages of the present invention more clearly understood, the present invention is further described in detail below in conjunction with examples and drawings. The exemplary embodiments of the present invention and their descriptions are only used to explain the present invention and are not intended to limit the present invention.

[0028] Example 1, as Figure 1-Figure 5 As shown, the present invention discloses a variable hydraulic oscillator for use in a downhole, comprising a cylindrical tube body 1 with a liquid flowing through its inner cavity, wherein a multi-stage rotating shaft type rotating disk group is movably provided in the cylindrical tube body 1, wherein the multi-stage rotating shaft type rotating disk group comprises a plurality of movable rotating disks 2 arranged at equal intervals along the axial direction of the cylindrical tube body 1, wherein the inner wall of the cylindrical tube body 1 is provided with a plurality of clamping grooves 3, wherein the movable rotating disk 2 is rotatably engaged with the plurality of clamping grooves 3 respectively through circumferentially arranged bosses 4, and wherein the movable rotating disk 2 comprises a hub 201, a rim 202 and a plurality of spokes 203. 03 is a wheel-shaped structure, and multiple spokes 203 are arranged between the hub 201 and the rim 202. The cross-section of the spokes 203 is inclined to the axis of the hub 201, and is used to drive the movable turntable 2 to rotate under the action of swirling water force and centrifugal force. A rotating shaft 5 horizontally facing the hub 201 is provided on the upper end of the connection surface between the spokes 203 and the hub 201, and a socket 6 for inserting the rotating shaft 5 is provided on the side wall of the hub 201. A torsion spring 7 is also sleeved on the rotating shaft 5 to rotate the spokes 203 back to their original position.

[0029] The sidewall of the hub 201 is provided with a number of engaging grooves 8 corresponding to the number of spokes 203. The engaging grooves 8 are arranged at an angle along the axial direction of the hub 201, and the socket 6 is provided in the middle of the upper end of the engaging grooves 8. Specifically, the axial inclination angle of the engaging grooves 8 is 15°, matching the angle of incidence of the swirling fluid. When the spokes 203 rotate, the direction of the combined force of the fluid impact force and the centrifugal force is parallel to the inclined surface of the engaging groove 3, thereby maximizing the conversion of the liquid flow energy into the rotational potential energy of the spokes 203. The socket 6 is located in the middle of the upper end of the engaging groove 3, forming a fulcrum for the rotation of the spokes 203. At low flow rates, the fluid driving force is amplified through the lever effect, thereby improving the initial starting torque. At high flow rates, a larger flow volume is released through the rotation of the spokes 203, ensuring that the spokes 203 can stably trigger radial vibration under different flow rates.

[0030] The lower end width of the engaging groove 8 is greater than the lower end width of the spoke 203. When the torsion spring 7 is not under force, the spoke 203 contacts the upper end surface of the inclined surface of the engaging groove 8. Specifically, the design of the gradually expanding engaging groove 8 forms an adaptive adjustment channel for fluid mechanics. When the kinetic energy of the fluid increases and the hydraulic torque exceeds the minimum driving force threshold of the torsion spring 7, the spoke 203 slides toward the bottom of the groove under the impact of the liquid flow, and the tilt angle automatically increases by 0-15°. At this time, the flow cross-sectional area increases by more than 20%, the compression of the torsion spring 7 increases, and the displacement of the spoke 203 triggers negative feedback regulation of the vibration amplitude, achieving vibration momentum fluctuations within a range of ±8%. This dynamic balancing mechanism enables the cylindrical tube body 1 to stably output radial vibration within a wide flow range of 3-15 L / s.

[0031] The cross-sections of the boss 4 and the slot 3 are both T-shaped, and the boss 4 is movably engaged with the slot 3. Specifically, the nested fit of the boss 4 and the slot 3 ensures that when the movable turntable 2 rotates within a limited range, it will not undergo relative displacement with the cylindrical tube 1. The dovetail-type contact surface effectively disperses radial loads and avoids local stress concentration. When the fluid flows through the inclined spokes 203, the movable turntable 2 can rotate freely, thereby achieving radial vibration.

[0032] A counterweight 9 is provided at the bottom of the rim 202, and the counterweight 9 does not contact the inner wall of the cylindrical tube 1. Specifically, the asymmetric counterweight design generates a controllable centrifugal force field through mass eccentricity. When the rotation speed of the movable turntable 2 reaches a critical value, the centrifugal force of the counterweight 9 generates a vector superposition at a specific phase angle, which can increase the radial vibration momentum by 2-3 times, ensuring the continuity of the vibration waveform and the energy transfer efficiency. The spokes 203 of the movable turntables 2 at each level have the same direction and angle. In a multi-stage shaft turntable group, the movable turntable 2 of the upper level can guide the movable turntable 2 of the lower level, thereby accelerating the rotation of the vortex of the lower level. The fluid movement between adjacent levels of the multi-stage structure will affect each other, and the displacement of the cylindrical tube 1 caused by the vibration will also cause mutual influence between the levels. Preferably, the counterweight 9 can be arranged on one side of the inner cavity of the rim 202, or on one side of the inner cavity of the boss 4. By optimizing the structure, the influence of the counterweight 9 on the external fluid can be reduced, thereby improving the smoothness of the overall structure, or reducing the resistance generated to the movable turntable 2 and increasing the amplitude effect.

[0033] There are three movable turntables 2, and the length of the counterweight 9 is no greater than the distance between any two movable turntables 2. Specifically, during the rotation of the movable turntable 2, the counterweight 9 will not interfere with the rotation of the movable turntable 2 at the lower end. The three-stage turntable group forms a resonance enhancement effect through a staggered arrangement with a phase difference of 120°. Combined with the setting of the counterweight 9, the vibration frequency can achieve energy superposition in the range of 100-500Hz. Experiments show that the three-stage structure improves the vibration energy efficiency by 180% compared with the single-stage structure, while avoiding the standing wave phenomenon caused by multi-stage interference.

[0034] Embodiment 2: Based on embodiment 1, this embodiment proposes a module with power generation function and radial vibration control.

[0035] like Figure 6 As shown, the top inner wall of the rim 202 is provided with an annular thread structure 10, and the upper end of the cylindrical tube body 1 is provided with a bevel gear rod 11 extending toward the multi-stage shaft-type turntable assembly. The bevel gear end of the bevel gear rod 11 is movably abutted and meshed with the annular thread structure 10. Specifically, during the meshing process, the transmission damping generated by the bevel gear pair directly acts on the rim 202 of the movable turntable 2, achieving a three-stage adjustment of "enhanced vibration, stable vibration, and vibration suppression." The helix angle of the annular thread structure 10 matches the bevel gear tooth profile to reduce meshing impact and improve transmission efficiency. At the same time, the axial force component of the thread structure is transmitted to the power generation module through the bevel gear rod 11, forming an axial preload compensation mechanism to avoid the risk of gear disengagement under high vibration conditions. When the power generation module is started, the magnetic coupling between the rotor on the power generation module and the rotating teeth 12 generates a reverse electromagnetic torque, which is transmitted in reverse to the movable turntable 2 through the bevel gear pair, forming a closed-loop speed control. For every 5 L / s increase in flow, power generation increases by 2-5 kW, while rotational speed decreases by 8-15%, achieving a dynamic balance between flow, power generation, and vibration. Downhole measurements have shown that this design can reduce drill string friction by 45% in horizontal well sections, increase WOB transmission efficiency by 30%, and increase single-trip drilling footage by 120 meters.

[0036] The control end of the bevel gear rod 11 is connected to a drive control module, which controls the axial movement of the bevel gear rod 11 along the cylindrical tube 1. Specifically, the drive control module has a built-in micro-hydraulic servo mechanism, which dynamically adjusts the axial vibration of the bevel gear rod 11 by real-time monitoring of the fluid pressure and vibration acceleration in the cylindrical tube 1. When the flow rate exceeds the set threshold (such as 15L / s), the module drives the bevel gear rod 11 toward the annular thread structure 10, so that the bevel gear and the annular thread structure 10 are in contact and engaged. At this time, the system converts 30%-50% of the rotational mechanical energy (about 5-20kW) into electrical energy. At the same time, the transmission damping effect of the gear pair reduces the speed of the movable turntable 2 by 15%-30%, achieving an amplitude attenuation of 40%-60%. The closed-loop control can ensure the stability of the vibration momentum.

[0037] One end of the drive control module is also provided with a power generation module, and a rotating tooth 12 is coaxially provided on the bevel gear rod 11, and a rotor that cooperates with the rotating tooth 12 is provided on the power generation module. Specifically, the power generation module adopts a magnetic coupling power generation system, that is, a non-contact design of a permanent magnet array and a stator winding. When the bevel gear rod 11 is engaged with the annular thread structure 10, the rotation of the movable turntable 2 drives the bevel gear rod 11 to rotate at a reduction ratio of 1:3.5 through the annular thread structure 10, driving the rotating tooth 12 to cut the magnetic flux lines at a speed of 200-1500rpm, generating 10-50V DC and storing it in a high-temperature resistant lithium battery pack. This process simultaneously generates a reverse electromagnetic torque, which reduces the driving torque of the movable turntable 2 by 20%-35%, forming a negative feedback regulation of the speed, thereby suppressing overload vibration.

[0038] When the bevel gear end engages with the annular threaded structure 10, the rotating teeth 12 engage with the rotor, and are used to convert the mechanical energy generated by the hydraulic energy-driven rotation of the multi-stage shaft-type turntable group into storable electrical energy. The multiple movable turntables 2 are fixedly connected by the central shaft 13. Specifically, when the movable turntables 2 are fixedly connected by the central shaft 13, the counterweights 9 on each movable turntable 2 are vertically aligned longitudinally, ensuring that the same centrifugal force is generated during rotation. The torque of the three-stage turntable is transmitted synchronously, which can improve energy conversion and avoid the situation where the energy transmission loss is large and the energy conversion is insufficient due to the single-stage energy transmission.

[0039] Embodiment 3: Based on Embodiment 1 and Embodiment 2, this embodiment proposes a specific working principle for a downhole variable hydraulic oscillator.

[0040] The specific implementation principle process is as follows:

[0041] Drilling fluid is injected from the top of the cylindrical tube 1 at a flow rate of 3-25 L / s. As it passes through the inclined spokes 203 (initial inclination 15°) of the first-stage movable turntable 2, it is guided by the spiral flow guide to form a swirling flow (peak flow rate of 8-12 m / s). The swirling flow impacts the spokes 203, creating a force parallel to the inclined surface of the engagement groove 8. This force drives the spokes 203 to rotate about the rotating axis 5, overcoming the preload force (50-100 N·m) of the torsion spring 7 and generating an initial centrifugal torque. When the fluid kinetic energy exceeds a threshold (corresponding to a flow rate ≥ 3 L / s), the movable turntable 2 begins to rotate (initial speed 200-500 rpm). The three-stage movable turntables 2 are arranged with a 120° phase shift. The swirling flow from the first-stage turntable is guided by the spokes 203, accelerating the rotation of the fluid in the secondary turntables, creating a cascade amplification effect. Experiments have shown that the superimposed vibration energy of the three-stage turntable is 180% higher than that of a single-stage one, extending the frequency range to 100-500 Hz.

[0042] Under low flow conditions (3-10 L / s), the fluid kinetic energy is low, and the spoke 203 maintains the initial inclination angle (15°) under the action of the torsion spring 7. At this time, the flow cross-sectional area is 80% of the reference value, the turntable speed is stable at 200-800 rpm, and the output basic radial vibration is (200-300 N·s).

[0043] Under medium to high flow conditions (10-15 L / s), the fluid impact force increases, the spoke 203 slides downward along the clamping groove 8, the inclination angle increases to 20-25 degrees, and the flow cross-sectional area expands to 120% of the reference value. At the same time, the centrifugal force enhances the eccentric effect of the counterweight 9, and the vibration momentum increases to 400-500 N·s.

[0044] Under overload conditions (>15 L / s), the inclination angle of spoke 203 reaches its maximum value (30°), the torsion spring 7 is compressed by 80%, and the flow cross-sectional area increases by 30%. At this point, the system triggers the amplitude negative feedback mechanism. The centrifugal force increases at a slower rate, and the turntable speed drops from 1500 rpm to 1000 rpm.

[0045] The vibration momentum is damped by 20-30% through spring damping, stabilizing it within the range of 400 ± 8% N·s. Simultaneously, the power generation module is activated. When the flow rate exceeds 15 L / s, the drive control module detects excessive vibration acceleration (>50 g) and activates a micro-hydraulic servo mechanism, which moves the bevel gear rod 11 axially by 2 mm, fully engaging the bevel gear end with the annular thread structure 10. The rotation of the movable turntable 2, via the annular thread structure 10 (6 mm pitch), drives the bevel gear rod 11 at a 1:4 reduction ratio. This drives the gears 12 to cut the permanent magnet array of the power generation module at a speed of 200-1500 rpm, generating 10-50 V DC (5-20 kW power) for storage in a high-temperature lithium battery pack. During power generation, the magnetic coupling between the gears 12 and the rotor generates a reverse electromagnetic torque (peak 300 N·m), which is transmitted to the movable turntable 2 via the bevel gear pair, reducing its speed by 15-30% (for example, from 1200 rpm to 850 rpm). According to the centripetal force formula F = mω²R, the square decay of the speed reduces the vibration momentum from 600N·s to 300N·s, and the amplitude fluctuation rate is compressed to ±5%.

[0046] By setting up a real-time monitoring system, the built-in optical fiber sensor on the central axis 13 collects the rotation speed (accuracy ±5rpm), phase difference (≤5°) and vibration stress (≤60% of the material yield strength) of the three-stage turntable in real time. The data is transmitted to the drive control module to realize automated detection and operation.

[0047] Of course, the present invention may have many other embodiments. Without departing from the spirit and essence of the present invention, those skilled in the art may make various corresponding changes and modifications based on the present invention, but these corresponding changes and modifications should all fall within the scope of protection of the claims attached to the present invention.

Claims

1. A variable hydraulic oscillator for use downhole, comprising a cylindrical tube (1) with a liquid flowing through its inner cavity, characterized in that: A multi-stage rotating shaft type turntable group is movably provided in the columnar tube body (1), the multi-stage rotating shaft type turntable group comprises a plurality of movable turntables (2) arranged at equal intervals along the axial direction of the columnar tube body (1), a plurality of clamping grooves (3) are provided on the inner wall of the columnar tube body (1), the movable turntable (2) is rotatably engaged with the clamping grooves (3), the movable turntable (2) comprises a wheel-shaped structure consisting of a hub (201), a rim (202) and a plurality of spokes (203), the cross section of the spokes (203) being arranged at an angle to the axis of the hub (201), and being used for driving the movable turntable (2) to rotate under the action of swirling water force and centrifugal force; The top inner side wall of the rim (202) is provided with an annular thread structure (10), the upper end of the columnar tube (1) is provided with a bevel gear rod (11) extending toward the multi-stage rotating shaft type turntable group, the bevel gear end of the bevel gear rod (11) is movably abutted and engaged with the annular thread structure (10), the control end of the bevel gear rod (11) is connected to a drive control module, one end of the drive control module is further provided with a power generation module, the bevel gear rod (11) is coaxially provided with a rotating tooth (12), and the power generation module is provided with a rotor that cooperates with the rotating tooth (12).

2. The variable hydraulic vibrator for underground use according to claim 1, characterized in that: A plurality of wheel spokes (203) are arranged between the wheel hub (201) and the wheel rim (202); a rotating shaft (5) facing horizontally toward the wheel hub (201) is provided on the upper end of the connection surface between the wheel spokes (203) and the wheel hub (201); a socket (6) for plugging the rotating shaft (5) is provided on the side wall of the wheel hub (201); a torsion spring (7) for rotating the wheel spokes (203) is also sleeved on the rotating shaft (5); a clamping groove (8) corresponding to the number of the plurality of wheel spokes (203) is provided on the side wall of the wheel hub (201); the clamping groove (8) is arranged obliquely along the axial direction of the wheel hub (201); and the socket (6) is arranged at the middle part of the upper end of the clamping groove (8).

3. The variable hydraulic vibrator for underground use according to claim 2, characterized in that: The width of the lower end of the clamping groove (8) is greater than the width of the lower end of the spoke (203), and the spoke (203) contacts the upper end surface of the inclined surface of the clamping groove (8) when the torsion spring (7) is not under force.

4. The variable hydraulic vibrator for underground use according to claim 1, characterized in that: The movable turntable (2) is rotatably engaged with a plurality of clamping slots (3) through circumferentially arranged bosses (4), the cross sections of the bosses (4) and the clamping slots (3) are both T-shaped structures, and the bosses (4) are movably engaged with the clamping slots (3).

5. The variable hydraulic vibrator for underground use according to claim 1, characterized in that: A counterweight (9) is provided at the bottom of the rim (202), and the counterweight (9) does not contact the inner wall of the columnar tube (1).

6. The variable hydraulic vibrator for underground use according to claim 5, characterized in that: Three movable turntables (2) are provided, and the length of the counterweight block (9) is not greater than the distance between any two movable turntables (2).

7. The variable hydraulic vibrator for underground use according to claim 1, characterized in that: The drive control module controls the axial movement of the bevel gear rod (11) along the columnar tubular body (1).

8. The variable hydraulic vibrator for underground use according to claim 7, characterized in that: When the bevel gear end is engaged with the annular thread structure (10), the rotating teeth (12) are engaged with the rotor, and are used to convert the mechanical energy of the multi-stage rotating shaft type rotating disk group driven by liquid energy into storable electrical energy. The plurality of movable rotating disks (2) are fixedly connected via a central shaft (13).

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