Gyroscope shock absorber with controllable rotating speed

Abstract

The invention belongs to the field of oil exploitation downhole tools, and discloses a gyro shock absorber with a controllable rotating speed. The shock absorber comprises a sleeve, a flow control mechanism, a turbine, a magnetic coupling mechanism and a shock absorption mechanism. The flow control mechanism is installed in the sleeve and provided with an overflowing hole, and the overflowing area of the overflowing hole can be changed so as to control the flow of fluid flowing through the overflowing hole. According to the gyroscope shock absorber, the flow control mechanism is matched with the turbine and the magnetic coupling mechanism to achieve the purpose of adjusting the rotating speed of the gyroscope in a liquid flow adjusting mode, the response speed is high, vibration in different directions and amplitudes can be sensed and responded more rapidly and accurately, the stability and the control capacity are higher, and the service life of the gyroscope shock absorber is prolonged. And a stable and reliable damping effect can be provided in various complex drilling environments.

Description

Technical Field

[0001] This invention relates to the field of downhole tools for oil extraction, and more particularly to a gyro damper with controllable rotation speed. Background Technology

[0002] During drilling operations, drill pipes generate various forms of vibration. These vibrations are mainly caused by two factors: the rotational movement of the drill pipe within the well and the movement of the drill bit when encountering hard formations. These vibrations not only affect drilling efficiency and quality but can also lead to problems such as wear and collapse of the drill pipe and wellbore. Therefore, the deployment and application of vibration damping devices in drilling operations are particularly crucial; their main function is to reduce the damage caused by bumps to the drill bit and drilling tools.

[0003] Patent CN2138694Y discloses an active vibration damper for drilling. The damper consists of a straight cylindrical body with upper and lower straight holes of different inner diameters, two pistons of different areas, a guide rod, a valve seat with a through hole at one end and a half-hole at the center, a valve stem, an elastic compression spring, an end cap, and an elastic damping support. When drilling mud flows into the upper cavity through the valve seat through hole, the pressure pushes the upper piston and guide rod downwards and the valve stem upwards, opening the pressure control valve. The mud flows into the lower cavity through the through hole on the guide rod and the radial hole at the bottom. When the force acting on the lower piston is balanced with the force on the upper piston, the pressure control valve remains stable, and the drill bit position remains stable. When an external disturbance force acts on the drill bit, it causes the guide rod to move up and down, resulting in a change in the position of the pressure control valve. This changes the force on the upper and lower pistons, and the resultant force is opposite to the direction of the guide rod's movement, forcing the guide rod to reduce vibration. However, the piston in this shock absorber has a large mass, and its inertia causes a certain delay in the shock absorber's response to external impacts.

[0004] Patent CN101775962A discloses an active vibration damper for oilfield drilling. This damper is fixedly installed inside the drill collar and includes a power source, a magnetic coupling mechanism, and a damping joint. The upper end of the magnetic coupling mechanism is connected to the power source, and the lower end is connected to the damping joint. The damping joint includes a damping shaft and an even number of semi-annular metal pendulum weights hinged to the damping shaft and spaced apart axially along the shaft. The magnetic coupling mechanism transmits the rotational motion of the power source to the damping shaft, thereby driving the pendulum weights to rotate. Under the action of their own inertia and centripetal force, the pendulum weights generate acceleration opposite to the direction of vibration, thus achieving vibration damping. However, because this damping method involves multiple parameters and complex dynamic characteristics, it is difficult to debug and maintain. Moreover, introducing pendulum weights for damping may change the dynamic characteristics of the system, thereby affecting the system's stability, limiting its applicability.

[0005] Patent CN204238873U discloses an internal spring shock absorber specifically for oil drilling. An upper connector is fixedly installed at the top of the shock absorber's outer column. A slide rail is installed in the center of the outer column, and a fixed outer sleeve is installed on the outer column. Bearing rollers are installed between the slide rail and the fixed outer sleeve, allowing the slide rail to rotate within the fixed outer sleeve. Upper and lower damping plates are installed within the slide rail and can slide up and down along it. Simultaneously, the rotation of the slide rail within the fixed outer sleeve allows the upper and lower damping plates to rotate. The punch pipe is divided into two parts: the upper half is fixedly installed on the upper damping plate, and the lower half is fixedly installed on the lower damping plate. Internal damping springs (four in total) are installed between the upper and lower damping plates, with the lower connector located at the bottom. This shock absorber utilizes internal springs to reduce drill bit vibration during drilling. However, the inertia of the springs causes a certain delay in the shock absorber's response to external impacts. This means that during drilling, when the drill bit is subjected to impact or vibration, the shock absorber may need a certain amount of time to adjust its damping force to effectively reduce the impact, thereby reducing its response speed and causing damage to the drill bit and drilling tools.

[0006] Therefore, there is still much room for improvement in the response speed and adaptability of current shock absorbers. Summary of the Invention

[0007] To address the aforementioned problems, this invention provides a gyroscope damper with controllable rotation speed, enabling rapid, controllable, and efficient adjustment of the gyroscope damper.

[0008] According to one aspect of the present invention, a gyro damper with controllable rotation speed is provided, comprising: The sleeve is cylindrical; A flow control mechanism is installed inside the sleeve and has a flow passage orifice. The flow area of ​​the flow passage orifice can be changed to control the flow rate of the fluid flowing through the flow passage orifice. A turbine, located below the flow control mechanism; A magnetic coupling mechanism, comprising an outer magnetic rotor and an inner magnetic rotor, wherein the outer magnetic rotor is fixedly connected to the turbine, and the inner magnetic rotor is located inside the outer magnetic rotor and is spaced apart from the outer magnetic rotor; A shock-absorbing mechanism, comprising a gyroscope and a gyroscope support assembly, wherein the gyroscope support assembly rotatably supports the gyroscope within the sleeve, and the upper end of the gyroscope is connected to and driven by the inner magnetic rotor to rotate.

[0009] According to one embodiment of the present invention, the flow control mechanism includes a static flow plate, a dynamic flow plate, and a driver. The static flow plate is fixedly installed inside the sleeve. The static flow plate is provided with a first flow passage hole. The dynamic flow plate is attached to one side of the static flow plate and can rotate relative to the static flow plate under the drive of the driver. The dynamic flow plate is provided with a second flow passage hole. The size of the overlapping area of ​​the first flow passage hole and the second flow passage hole determines the flow area.

[0010] According to one embodiment of the present invention, the static flow plate has an axially extending mounting shaft at its center, and the dynamic flow plate has a mounting hole at its center, the mounting hole being able to fit onto the mounting shaft to assemble the static flow plate and the dynamic flow plate together.

[0011] According to one embodiment of the present invention, the flow control mechanism further includes a fixing cap, the end of the mounting shaft is provided with an external thread, the fixing cap is provided with an internal thread, and the fixing cap is threadedly connected to the mounting shaft to hold the dynamic flow plate on the static flow plate by means of the fixing cap.

[0012] According to one embodiment of the present invention, the outer periphery of the flow disk is provided with teeth, and the output shaft of the driver is provided with a gear, the teeth of the gear meshing with the teeth of the flow disk to drive the flow disk to rotate.

[0013] According to one embodiment of the present invention, the first flow passage includes N fan-shaped holes evenly distributed along the circumference of the static flow disk, and the second flow passage includes N fan-shaped holes evenly distributed along the circumference of the dynamic flow disk, wherein the radial positions of the first flow passage and the second flow passage correspond to each other, and N≥2.

[0014] According to one embodiment of the present invention, a portion of the outer periphery of the flow disk is provided with teeth, and the toothed portion spans an angle range of not less than 360° / N.

[0015] According to one embodiment of the present invention, the flow control mechanism further includes a flow sensor disposed near the turbine and used to measure the fluid flow rate near the turbine.

[0016] According to one embodiment of the present invention, the flow control mechanism further includes a controller, which is communicatively connected to the flow sensor and the driver, and the controller operates the driver based on the fluid flow rate detected by the flow sensor.

[0017] According to one embodiment of the present invention, the gyro damper further includes a flow guiding mechanism disposed between the flow control mechanism and the turbine, the flow guiding mechanism being used to uniformly disperse fluid circumferentially and guide it to the turbine.

[0018] According to one embodiment of the present invention, the flow guiding mechanism is a flow guiding sleeve, wherein the upper section of the flow guiding sleeve is conical and the lower section is cylindrical.

[0019] According to one embodiment of the present invention, the gyro damper further includes a pressure balancing mechanism, which includes a valve body and a valve core. The valve body is disposed in the lower section of the flow guide sleeve, and the valve core is disposed in the valve body. The upper section of the flow guide sleeve is provided with a flow guide hole. The valve core moves up and down under the action of the pressure difference between the inside and outside of the valve body to balance the pressure and flow rate of the fluid in the sleeve.

[0020] According to one embodiment of the present invention, the external magnetic rotor includes a plurality of external magnetic elements, and the inner wall of the cylinder of the turbine is provided with a plurality of mounting slots for accommodating the plurality of external magnetic elements, the plurality of mounting slots being evenly spaced in the circumferential direction.

[0021] According to one embodiment of the present invention, the inner magnetic rotor includes a plurality of inner magnetic elements, which cooperate with the plurality of outer magnetic elements, and there is an air gap between them and an isolation sleeve is provided.

[0022] According to one embodiment of the present invention, the damping mechanism further includes a speed increaser, the input of which is connected to the inner magnetic rotor and the output of which is connected to the gyroscope.

[0023] According to one embodiment of the present invention, the speed increaser employs a planetary gear set.

[0024] According to one embodiment of the present invention, the gyroscope support assembly includes a positioning sleeve, a straightening sleeve, and a bearing. The positioning sleeve is supported on the inner wall of the sleeve, the straightening sleeve abuts against the inner side of the positioning sleeve, and the bearing is used to rotatably support the gyroscope within the straightening sleeve.

[0025] According to one embodiment of the present invention, the gyroscope damper further includes a hollow return connector located below the gyroscope. The annular space between the lower section of the return connector and the sleeve is a sealed structure. A return groove is provided in the middle section of the side wall of the return connector, and the return groove connects the internal hollow area of ​​the return connector with the external annular area.

[0026] By adopting the above technical solutions, the speed-controllable gyro damper provided by this invention has at least the following advantages compared with the prior art: (1) By using the combination of the flow control mechanism, turbine and magnetic coupling mechanism, the purpose of adjusting the gyroscope speed by means of liquid flow regulation is achieved. It has a fast response speed, can sense and respond to vibrations of different directions and amplitudes more quickly and accurately, has stronger stability and control capabilities, and can provide stable and reliable vibration reduction effect in various complex drilling environments. (2) The turbine and the damping mechanism rely on a magnetic coupling mechanism for torque transmission. The magnetic coupling mechanism effectively transmits the turbine kinetic energy to the gyroscope, achieving efficient energy conversion. Through this combination, the turbine can make fuller use of liquid kinetic energy and convert it into mechanical energy, thereby improving energy utilization efficiency, avoiding friction loss and mechanical wear in mechanical transmission, and improving the reliability and durability of the system. (3) Using gyroscope vibration reduction technology, the inertial force generated by the high-speed rotation of the gyroscope is used to offset or reduce the vibration of the system. This method can effectively reduce the vibration amplitude of the system and achieve a high-efficiency vibration reduction effect. It can reduce vibration in multiple axes and is suitable for vibration control in different dimensions and directions. Attached Figure Description

[0027] The accompanying drawings are provided to further illustrate the present disclosure and form part of the specification. They are used together with the following detailed description to explain the present disclosure, but do not constitute a limitation thereof. In the drawings: Figure 1 This is a schematic diagram of the overall structure of a speed-controllable gyro damper according to an embodiment of the present invention; Figure 2 This is a schematic diagram of the flow control mechanism according to an embodiment of the present invention; Figure 3 This is an assembly diagram of a flow control mechanism according to an embodiment of the present invention; Figure 4 This is a schematic diagram of the structure of a static flow disk according to an embodiment of the present invention; Figure 5 This is a schematic diagram of the structure of a flow disk according to an embodiment of the present invention.

[0028] List of reference numerals in the attached diagram: 10. Sleeve; 11. Upper connector; 12. Lower connector; 20. Flow control mechanism; 21. Static flow plate; 21a. First flow passage hole; 21b. Mounting shaft; 21c. Fixing cap; 22. Dynamic flow plate; 22a. Second flow passage hole; 22b. Mounting hole; 22c. Gear; 23. Driver; 23a. Pinion; 24. Flow sensor; 30. Turbine; 40. Magnetic coupling mechanism; 41. Outer magnetic rotor; 42. Inner magnetic rotor; 43. 44. Rotor first bearing; 45. Rotor second bearing; 50. Rotor bushing; 51. Shock absorption mechanism; 51. Gyroscope; 51a. Gyroscope body; 51b. Outer shell; 51c. Gyroscope second bearing; 52. Positioning sleeve; 53. Straightening sleeve; 54. Gyroscope first bearing; 55. Second bushing; 60. Flow guiding mechanism; 70. Pressure balancing mechanism; 71. Valve body; 72. Valve core; 80. Speed ​​increaser; 90. Return connector; 91. Return groove. Detailed Implementation

[0029] To make the objectives, technical solutions, and advantages of this invention clearer, the invention will be further described in detail below with reference to specific embodiments. It should be understood that the specific embodiments described herein are merely illustrative and not intended to limit the invention.

[0030] The terms "comprising" and "having," and any variations thereof, used in the specification and accompanying drawings of this invention are intended to cover non-exclusive inclusion; the terms "first," "second," etc., used in the specification, claims, or accompanying drawings of this invention are used to distinguish different objects, not to describe a particular order. "A plurality of" means two or more, unless otherwise explicitly specified.

[0031] In the description of this invention and the above-described drawings, when an element is referred to as "fixed to," "mounted to," "set on," or "connected to" another element, it can be located directly or indirectly on that other element. For example, when an element is referred to as "connected to" another element, it can be directly or indirectly connected to that other element.

[0032] Furthermore, the reference to "embodiment" herein means that a particular feature, structure, or characteristic described in connection with an embodiment may be included in at least one embodiment of the invention. The appearance of this phrase in various places throughout the specification does not necessarily refer to the same embodiment, nor is it a separate or alternative embodiment mutually exclusive with other embodiments. It will be explicitly and implicitly understood by those skilled in the art that the embodiments described herein can be combined with other embodiments.

[0033] The purpose of this invention is to provide a gyroscope damper with controllable rotation speed. Figure 1 A schematic diagram of the overall structure of a speed-controllable gyro damper according to an embodiment of the present invention is shown. The gyro damper generally includes a sleeve 10, a flow control mechanism 20, a turbine 30, a magnetic coupling mechanism 40, and a damping mechanism 50.

[0034] The sleeve 10 forms a housing for accommodating other components and creates a channel for liquid flow. The sleeve 10 may be a hollow cylinder that extends axially for a certain length to accommodate other components.

[0035] The flow control mechanism 20 is used to regulate the flow rate of the liquid flowing to the turbine 30. The flow control mechanism 20 is installed inside the sleeve 10. The flow control mechanism 20 has a flow passage, the flow area of ​​which can be changed to control the flow rate of the fluid flowing through the flow passage. In some embodiments, the flow control mechanism includes a static flow plate, a dynamic flow plate, and a driver.

[0036] Figure 2 A schematic diagram of a flow control mechanism according to an embodiment of the present invention is shown. Figure 3 An assembly diagram of the flow control mechanism is shown. Figure 4 A schematic diagram of the static flow plate is shown. Figure 5 A schematic diagram of the dynamic flow disk is shown.

[0037] The flow plate 21 is fixedly installed inside the sleeve. For example, the inner wall of the sleeve 10 may have an inwardly protruding inner step, and the portion of the sleeve 10 above the inner step may have an internal thread. An upper connector 11 can be connected to the upper end of the sleeve 10. The lower end of the upper connector 11 has an external thread, which can form a threaded connection with the internal thread at the upper end of the sleeve 10. The outer edge of the flow plate 21 can be placed on the inner step of the sleeve 10. When the upper connector 11 is assembled to the upper end of the sleeve 10, the bottom of the upper connector 11 abuts and presses against the upper flow plate 21. Therefore, the flow plate 21 is clamped between the inner step of the sleeve 10 and the bottom of the upper connector 11, thereby fixing the flow plate 21 inside the sleeve 10. The upper connector 11 is also a hollow structure, and its sidewalls do not obstruct the flow passage of the flow plate 21.

[0038] refer to Figure 4 The static flow plate 21 is provided with a first flow passage 21a. In some embodiments, the first flow passage 21a includes N fan-shaped holes evenly distributed along the circumference of the static flow plate 21. The number and size of the fan-shaped holes can be determined according to the specific application environment. An axially extending mounting shaft 21b is provided at the center of one side of the static flow plate 21, and the mounting shaft 21b is used to mount the dynamic flow plate 22. For example, the center of the dynamic flow plate 22 is provided with a mounting hole 22b, which can be fitted onto the mounting shaft 21b to assemble the static flow plate 21 and the dynamic flow plate 22 together. Optionally, in some embodiments, in order to rotatably mount the dynamic flow plate 22 onto the static flow plate 21, the end of the mounting shaft 21b can be provided with an external thread, and the dynamic flow plate 22 can be rotatably held on the static flow plate 21 by using a fixing cap 21c with an internal thread.

[0039] refer to Figure 2 and Figure 5 The moving flow plate 22 is attached to one side of the stationary flow plate 21. The moving flow plate 22 is provided with a second flow passage 22a, which may include N fan-shaped holes evenly distributed along the circumference of the moving flow plate 22. The second flow passage 22a corresponds to the first flow passage 21a in radial position and has the same number. The size of the overlapping area of ​​the first flow passage 21a and the second flow passage 22a determines the flow area through which the fluid can flow. In a specific embodiment, the stationary flow plate 21 is provided with three first flow passages 21a, and correspondingly, the moving flow plate 22 is provided with three second flow passages 22a.

[0040] The outer diameter of the moving flow disk 22 is smaller than the outer diameter of the stationary flow disk 21. The moving flow disk 22 can rotate relative to the stationary flow disk 21 under the drive of the driver 23. Figure 2 , Figure 3 and Figure 5As shown, the outer periphery of the moving flow disk 22 is provided with teeth 22c. A pinion 23a is provided on the output shaft of the driver 23. The teeth of the pinion 23a mesh with the teeth 22c of the moving flow disk 22, allowing the moving flow disk 22 to rotate relative to the stationary flow disk 21 under the drive of the driver 23. When the moving flow disk 22 rotates relative to the stationary flow disk 21, the relative positions of the first flow hole 21a and the second flow hole 22a change, causing the size of their overlapping area to change, thereby altering the flow area.

[0041] In some embodiments, the entire outer periphery of the flow plate 22 is provided with teeth 22c. In other embodiments, a portion of the outer periphery of the flow plate 22 is provided with teeth, and the toothed portion spans an angle range of not less than 360° / N. Since the flow plate 22 can achieve adjustment of the flow area from zero to maximum by rotating only within an angle range of 360° / N, the adjustment requirements can be met when the angle range spanned by the toothed portion is not less than 360° / N.

[0042] The driver 23 can be a motor, and the motor housing can be fixedly installed on the inner wall of the sleeve 10.

[0043] The turbine 30 is used to convert the energy of liquid flow into usable mechanical energy. The turbine 30 is disposed within the sleeve 10 and below the flow control mechanism 20. The turbine 30 has a cylinder with multiple blades externally mounted on the cylinder. These blades are designed to efficiently capture the kinetic energy of the fluid. When the liquid impacts the turbine blades, it causes the turbine to rotate, converting the kinetic energy of the liquid into the mechanical energy of the turbine 30.

[0044] Optionally, in some embodiments, the gyro damper further includes a flow guiding mechanism 60. The flow guiding mechanism 60 is disposed between the flow control mechanism 20 and the turbine 30. The flow guiding mechanism 60 is used to uniformly disperse and guide the fluid circumferentially to the turbine 30.

[0045] For example, the flow guiding mechanism 60 can be a flow guiding sleeve, with the upper section being a tapered shape that gradually expands from top to bottom, and the lower section being a straight cylinder. The outer diameter of the lower section of the flow guiding sleeve is similar to the outer diameter of the turbine 30 cylinder, and the lower section of the flow guiding sleeve is connected to the turbine 30 cylinder. The liquid flowing downward from the flow control mechanism 20 through the flow hole is concentrated in the area where the flow hole is located. If it directly impacts the turbine 30 blades, it may cause the turbine 30 to vibrate due to excessive and uneven flow, affecting the overall stability of the shock absorber. By setting up the flow guiding sleeve, the liquid flowing downward from the flow hole first impacts the upper section of the flow guiding sleeve, is buffered in the upper section and dispersed circumferentially, and then flows down the lower section to the turbine blades.

[0046] Optionally, in some embodiments, the gyro damper further includes a pressure balancing mechanism 70. The pressure balancing mechanism 70 may include a valve body 71 and a valve core 72. The valve body 71 may be disposed within the lower section of the flow guide sleeve. The valve body 71 may be a cylindrical structure with an open top and a closed bottom. The valve core 72 may be disposed within the valve body 71; for example, the valve core 72 may be a piston, which seals against the side wall of the valve body 71 to form a sealed air chamber between the piston and the bottom surface of the valve body 71. The upper section of the flow guide sleeve is provided with a flow guide hole, through which liquid can enter the valve body 71 and act on the valve core 72. The valve core moves up and down under the action of the pressure difference between the inside and outside of the valve body to balance the pressure and flow rate of the fluid within the sleeve 10. The valve body 71 and valve core 72 can improve the stability and reliability of the system. By balancing the internal flow and pressure distribution, they can prevent the fluid from having excessively high or low flow rates and pressures in the sleeve 10, thereby reducing pipeline vibration and noise, extending the service life of the system, and providing a buffer inside the shock absorber to prevent it from bearing excessive pressure, thus ensuring the stable and efficient operation of the system under different working conditions.

[0047] The magnetic coupling mechanism 40 is used to achieve contactless power transmission between the turbine 30 and the gyroscope 51. The magnetic coupling mechanism 40 generally includes an outer magnetic rotor 41 and an inner magnetic rotor 42.

[0048] The external magnetic rotor 41 may include multiple external magnetic elements, which may be permanent magnets. The inner wall of the turbine 30 cylinder is provided with multiple mounting slots for accommodating these external magnetic elements, and these slots are evenly spaced circumferentially. The mounting slots may extend a certain distance axially. The number and position of the mounting slots can be determined according to the required number and arrangement of the external magnetic elements of the external magnetic rotor 41. By accommodating the external magnetic elements of the external magnetic rotor 41 within the mounting slots of the turbine 30 cylinder, it is ensured that the external magnetic elements will not move or loosen during operation. This design not only ensures a good match between the external magnetic rotor 41 and the turbine 30, but also helps reduce the imbalance and vibration of the turbine 30, thereby extending the service life of the equipment and improving operational stability and reliability, more effectively converting liquid kinetic energy into mechanical energy, and improving energy conversion efficiency.

[0049] The inner magnetic rotor 42 may include multiple inner magnetic elements, which may be permanent magnets. These inner magnetic elements are magnetically coupled to multiple outer magnetic elements. An air gap is provided between the outer magnetic rotor 41 and the inner magnetic rotor 42, and an isolation sleeve may be installed. When the turbine 30 rotates, it drives the outer magnetic rotor 41 in the magnetic coupling mechanism 40 to rotate. The magnetic field generated by the permanent magnet on the outer magnetic rotor 41 interacts with the permanent magnet on the inner magnetic rotor 42 through the working air gap, generating magnetic field coupling. This magnetic field coupling causes the inner magnetic rotor 42 to also begin to rotate, thus achieving contactless power transmission. By providing an air gap between the inner magnetic rotor 42 and the outer magnetic rotor 41, physical separation between them can be ensured. This means that even under high-speed rotation, the two will not directly contact each other, which helps maintain the stability and efficiency of the system. It reduces undesirable interactions between the inner magnetic rotor 42 and the outer magnetic rotor 41, reduces wear and friction, ensures the smooth operation of the energy conversion process, improves the energy utilization rate of the system, and extends the service life of the equipment.

[0050] The upper and lower ends of the inner magnetic rotor 42 are supported by a first rotor bearing 43 and a second rotor bearing 44, respectively. Optionally, the guide sleeve and the cylinder of the turbine 30 are connected via a rotor bushing 45. The first rotor bearing 43 can be disposed between the rotor bushing 45 and the inner magnetic rotor 42. The rotor bushing 45 can form a barrier for the first rotor bearing 43, preventing impurities such as mud from entering the bearing and reducing corrosion and damage to the bearing.

[0051] The damping mechanism 50 is the core component for achieving damping. The damping mechanism 50 mainly includes a gyroscope 51 and a gyroscope support assembly. The gyroscope support assembly is used to rotatably support the gyroscope 51 within the casing 10. In some embodiments, the gyroscope support assembly includes a positioning sleeve 52, a centering sleeve 53, and a first gyroscope bearing 54. The positioning sleeve 52 is supported on the inner wall of the casing 10 and is used to achieve radial positioning of the gyroscope 51 within the casing 10. The centering sleeve 53 abuts against the inner side of the positioning sleeve 52 and is used to prevent the gyroscope 51 from bending and deforming during drilling, thereby protecting the gyroscope 51 from damage. The first gyroscope bearing 54 is used to rotatably support the gyroscope 51 within the centering sleeve 53.

[0052] The gyroscope 51 may include a gyroscope body 51a and a shell 51b. The shell 51b is fitted onto the lower section of the gyroscope body 51a, and a second gyroscope bearing 51c is provided between the two, thereby enabling the gyroscope body 51a to rotate relative to the shell 51b. A stabilizing sleeve 53 is fitted onto the upper section of the gyroscope body 51a. The upper section of the shell 51b is connected to the lower section of the stabilizing sleeve 53, together ensuring the stability and shock absorption of the gyroscope body 51a during high-speed rotation. The upper end of the stabilizing sleeve 53 is located near the upper end of the gyroscope body 51a. A second bushing 55 is provided between the upper end of the stabilizing sleeve 53 and the lower end of the turbine 30 cylinder. The inner wall of the upper end of the second bushing 55 has a radially protruding step, and a second rotor bearing 44 is provided on the step. The cylinder of the turbine 30, the outer magnetic rotor 41, and the inner magnetic rotor 42 can all be rotatably supported on the second rotor bearing 44. The lower end of the second bushing 55 is provided with an internal thread, which forms a threaded connection with the external thread at the upper end of the straightening sleeve 53. A lower step is provided on the inner wall of the lower end of the second bushing 55, and an installation groove is formed between the lower step and the top end of the straightening sleeve 53. The first bearing 54 of the gyroscope can be installed in the installation groove. The top end of the gyroscope body 51a is installed in the first bearing 54 of the gyroscope, and the top end of the gyroscope body 51a is connected to the inner magnetic rotor 42 for transmission.

[0053] When the internal magnetic rotor 42 drives the gyroscope body 51a to rotate at high speed, energy can be transferred to the surrounding structure through the rotational inertia. This energy transfer helps to balance and offset the vibrations and shocks generated during drilling, thereby achieving a shock absorption effect. Moreover, the gyroscope body 51a is constantly rotating, allowing the shock absorber to respond quickly to changes during the drilling process and continuously provide shock absorption without reducing performance due to extended working time or changes in external conditions.

[0054] Optionally, in some embodiments, the damping mechanism may further include a speed increaser 80, which may be disposed in the second bushing 55. The input end of the speed increaser 80 is connected to the inner magnetic rotor 42, and the output end of the speed increaser 80 is connected to the upper end of the gyroscope body 51a. The speed increaser 80 may be a planetary gear set. The speed increaser 80 is used to smoothly increase the rotational speed. The planetary gear set may use ground high-precision gears to achieve smooth, low-noise, high-torque, high-temperature resistant, and long-life operation. The inner magnetic rotor 42 provides rotational power, which, after being increased in speed by the speed increaser 80, drives the gyroscope body 51a to rotate at high speed, thereby improving the vibration damping effect.

[0055] Optionally, in some embodiments, the gyroscope damper further includes a return connector 90. The return connector 90 is located below the gyroscope 51 and is a hollow cylindrical shape. The annulus between the lower section of the return connector 90 and the sleeve 10 is a sealed structure. A return groove 91 is provided in the middle section of the side wall of the return connector 90, which connects the internal hollow area of ​​the return connector 90 with the external annular area. The return connector 90 may have multiple return grooves 91, which are evenly distributed circumferentially. If the liquid flowing in the annulus between the gyroscope housing 51b and the sleeve 10 directly enters the next tool section, it may generate a large impact force. The return connector 90 is provided so that the liquid in the annulus enters the interior of the return connector 90 from the return grooves 91, thus buffering the liquid. The upper end of the return connector 90 can be connected to the lower end of the gyroscope housing 51b, and its lower end is connected to the lower connector 12.

[0056] Optionally, in some embodiments, the flow control mechanism 20 may further include a flow sensor 24, which may be located near the turbine 30 and used to measure the fluid flow rate near the turbine 30. For example, to facilitate external communication, the flow sensor 24 may be installed on the inner wall of the sleeve 10, near the tapered portion of the guide sleeve. The flow rate of the liquid near the turbine 30 can be obtained through the flow sensor 24, and the flow area can be adjusted according to the flow rate and vibration conditions.

[0057] Optionally, in some embodiments, the flow control mechanism 20 may further include a controller. The controller is communicatively connected to the flow sensor 24 and the actuator 23. The controller may store flow velocity information corresponding to different vibration levels. The controller may operate the actuator 23 based on the difference between the fluid flow rate information detected by the flow sensor 24 and the set flow rate corresponding to the current vibration level, thereby changing the flow area.

[0058] The rotational speed of the gyroscope 51 can be adjusted by manually or automatically changing the action of the driver 23. Manual adjustment can be performed based on the operator's experience and the fluid flow information detected by the flow sensor 24.

[0059] The internal adjustment process of this gyroscope shock absorber is illustrated below using the example of the controller automatically adjusting the rotational speed of gyroscope 51. When vibration is encountered and damping is required, the controller determines the expected fluid (drilling fluid) flow rate based on the current vibration magnitude. The controller further determines the operating range of the actuator 23 based on the difference between the drilling fluid flow rate detected by the flow sensor 24 and the expected flow rate. The controller controls the actuator 23 to operate according to the determined operating range. The actuator 23 drives the pinion 23a on the output shaft to rotate, which in turn drives the flow disk 22 meshing with the pinion 23a to rotate. The rotation of the flow disk 22 changes the flow area through which the drilling fluid can flow. The change in drilling fluid flow rate causes a change in the rotational speed of turbine 30, which in turn changes the rotational speed of the outer magnetic rotor 41 connected to turbine 30. This causes a change in the rotational speed of the inner magnetic rotor 42 and the gyroscope body 51a connected to the inner magnetic rotor 42. When the gyroscope body 51a rotates at high speed, energy can be transferred to the surrounding structure through rotational inertia. This energy transfer helps to balance and offset the vibrations and impacts generated during drilling, thereby achieving a damping effect.

[0060] The embodiments described above are merely illustrative of implementation methods of the present invention, and while the descriptions are specific and detailed, they should not be construed as limiting the scope of the present invention. It should be noted that those skilled in the art can make various modifications and improvements without departing from the concept of the present invention, and these modifications and improvements all fall within the scope of protection of the present invention.

Claims

1. A gyroscope damper with controllable rotation speed, characterized in that, include: The sleeve is cylindrical; A flow control mechanism is installed inside the sleeve and has a flow passage orifice. The flow area of ​​the flow passage orifice can be changed to control the flow rate of the fluid flowing through the flow passage orifice. The turbine is located below the flow control mechanism; A magnetic coupling mechanism, comprising an outer magnetic rotor and an inner magnetic rotor, wherein the outer magnetic rotor is fixedly connected to the turbine, and the inner magnetic rotor is located inside the outer magnetic rotor and is spaced apart from the outer magnetic rotor; A shock-absorbing mechanism, comprising a gyroscope and a gyroscope support assembly, wherein the gyroscope support assembly rotatably supports the gyroscope within the sleeve, and the upper end of the gyroscope is connected to and driven by the inner magnetic rotor to rotate.

2. The gyro damper with controllable rotation speed according to claim 1, characterized in that, The flow control mechanism includes a static flow plate, a dynamic flow plate, and a driver. The static flow plate is fixedly installed inside the sleeve. The static flow plate has a first flow passage hole. The dynamic flow plate is attached to one side of the static flow plate and can rotate relative to the static flow plate under the drive of the driver. The dynamic flow plate has a second flow passage hole. The size of the overlapping area of ​​the first flow passage hole and the second flow passage hole determines the flow area.

3. The speed-controllable gyro damper according to claim 2, characterized in that, The static flow plate has an axially extending mounting shaft at its center, and the dynamic flow plate has a mounting hole at its center. The mounting hole can be fitted onto the mounting shaft to assemble the static flow plate and the dynamic flow plate together.

4. The speed-controllable gyro damper according to claim 3, characterized in that, The flow control mechanism also includes a fixing cap. The end of the mounting shaft is provided with an external thread, and the fixing cap is provided with an internal thread. The fixing cap is threadedly connected to the mounting shaft to hold the dynamic flow plate on the static flow plate.

5. The speed-controllable gyro damper according to claim 3, characterized in that, The outer periphery of the flow disk is provided with teeth, and the output shaft of the driver is provided with a gear. The teeth of the gear mesh with the teeth of the flow disk to drive the flow disk to rotate.

6. The speed-controllable gyro damper according to claim 5, characterized in that, The first flow passage includes N fan-shaped holes evenly distributed along the circumference of the static flow plate, and the second flow passage includes N fan-shaped holes evenly distributed along the circumference of the dynamic flow plate. The radial positions of the first flow passage and the second flow passage correspond to each other, where N≥2.

7. The speed-controllable gyro damper according to claim 6, characterized in that, A portion of the outer periphery of the flow disk is provided with teeth, and the angular range spanned by the toothed portion is not less than 360° / N.

8. The speed-controllable gyro damper according to claim 2, characterized in that, The flow control mechanism also includes a flow sensor, which is located near the turbine and is used to measure the fluid flow rate near the turbine.

9. The speed-controllable gyro damper according to claim 8, characterized in that, The flow control mechanism also includes a controller, which is communicatively connected to the flow sensor and the driver, and operates the driver based on the fluid flow rate detected by the flow sensor.

10. The speed-controllable gyro damper according to claim 1, characterized in that, The gyro damper also includes a flow guiding mechanism, which is disposed between the flow control mechanism and the turbine. The flow guiding mechanism is used to uniformly disperse the fluid in the circumferential direction and guide it to the turbine.

11. The speed-controllable gyro damper according to claim 10, characterized in that, The flow guiding mechanism is a flow guiding sleeve, the upper section of which is conical and the lower section is cylindrical.

12. The speed-controllable gyro damper according to claim 11, characterized in that, The gyro damper also includes a pressure balancing mechanism, which includes a valve body and a valve core. The valve body is located in the lower section of the flow guide sleeve, and the valve core is located in the valve body. The upper section of the flow guide sleeve is provided with a flow guide hole. The valve core moves up and down under the action of the pressure difference between the inside and outside of the valve body to balance the pressure and flow rate of the fluid in the sleeve.

13. The speed-controllable gyro damper according to claim 1, characterized in that, The external magnetic rotor includes multiple external magnetic elements, and the inner wall of the turbine cylinder is provided with multiple mounting slots for accommodating the multiple external magnetic elements. The multiple mounting slots are evenly spaced in the circumferential direction.

14. The speed-controllable gyro damper according to claim 13, characterized in that, The inner magnetic rotor includes multiple inner magnetic elements, which cooperate with multiple outer magnetic elements, and there is an air gap between them and an isolation sleeve.

15. The speed-controllable gyro damper according to claim 1, characterized in that, The damping mechanism also includes a speed increaser, the input of which is connected to the internal magnetic rotor and the output of which is connected to the gyroscope.

16. The speed-controllable gyro damper according to claim 15, characterized in that, The speed increaser uses a planetary gear set.

17. The speed-controllable gyro damper according to claim 1, characterized in that, The gyroscope support assembly includes a positioning sleeve, a straightening sleeve, and a bearing. The positioning sleeve is supported on the inner wall of the sleeve, the straightening sleeve abuts against the inner side of the positioning sleeve, and the bearing is used to rotatably support the gyroscope inside the straightening sleeve.

18. The speed-controllable gyro damper according to claim 1, characterized in that, The gyroscope damper also includes a hollow return connector located below the gyroscope. The annular space between the lower section of the return connector and the sleeve is a sealed structure. A return groove is provided in the middle section of the side wall of the return connector, which connects the internal hollow area of ​​the return connector with the external annular area.

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