Drill bit vibration suppression pushing mechanism flow-induced thrust characteristic verification test bed and test method thereof

Abstract

The application discloses a drill bit vibration suppression pushing mechanism flow-induced thrust characteristic verification test bed and a test method thereof. The test bed comprises a pushing mechanism assembly, a fluid injection mechanism, a sensor assembly and a data acquisition and processing system; the abutting column is coaxially installed in the inner cavity of the simulated outer shell and forms an annular flow gap, the water pump pressurizes and injects the fluid into the inner cavity, the fluid passes through the flow gap to generate an axial thrust on the abutting column, and the disc spring provides a reset elastic force after the pressure is removed; the sensor assembly detects the thrust and displacement, and the data acquisition and processing system synchronously collects parameters and generates a water pressure-displacement-pressure characteristic curve. The test method sequentially performs parameter configuration, baseline calibration, step-by-step pressurization test, curve generation analysis and parameter optimization iteration, replaces the abutting columns and the disc springs of different specifications to verify the flow-induced thrust characteristic, compares the lift and drop pressure hysteresis difference to evaluate the reset performance of the disc spring, and provides experimental data support for the design of a target intelligent drill bit vibration suppression execution mechanism.

Description

Technical Field

[0001] This application relates to the field of oil drilling tool testing technology, specifically to a test bench and test method for verifying the flow-induced thrust characteristics of a drill bit vibration suppression and pushing mechanism. Background Technology

[0002] In oil drilling engineering, stick-slip vibration is a key problem leading to increased drill bit wear and reduced drilling efficiency. To solve this technical problem, a smart drill bit that can suppress stick-slip vibration has been proposed in related technologies. One of the core components of this smart drill bit is a vibration damping actuator, which works as follows: High-pressure drilling fluid flows into the guide channel inside the drill bit body and flows upward through the annular gap between the abutment post and the inner wall of the guide perforation. The flowing drilling fluid generates an upward axial thrust on the abutment post, pushing it to overcome the spring force of the reset disc spring and extend outward (radially), so that the end face of the abutment post touches the well wall of the formation, generating a damping reaction force, thereby suppressing the stick-slip vibration of the drill bit; when the drilling fluid pressure is removed, the disc spring pushes the abutment post to retract.

[0003] Before the above-mentioned vibration damping actuators are implemented in engineering, the following key parameter selection issues urgently need to be verified through experiments: (1) The size of the annular flow gap directly determines the flow-thrust relationship. The thrust characteristics of different gap size schemes are difficult to predict accurately by theoretical calculation alone. (2) The spring constant directly affects the response speed and reset reliability of the abutment post, and it is necessary to systematically screen various spring parameter schemes under laboratory conditions; (3) The external constraint force on the abutment column is different under different strata confining pressure conditions. It is necessary to evaluate the influence of the constraint force on the flow-induced thrust-displacement characteristics. (4) In actual drilling conditions, the drilling fluid pressure output by the mud pump is not constant, but there is a periodic pulsation related to the pump frequency. This pulsating pressure may cause the dynamic oscillation response of the abutment column. If the natural frequency of the disc spring-abutment column system is close to the pump pulsation frequency, resonance may occur, affecting the vibration suppression effect or even causing the mechanism to fail. (5) During the drilling process, the drill bit generates a large amount of cutting heat when cutting the rock. This cutting heat is conducted through the drill bit body to the area where the push mechanism is located, causing the temperature in this area to rise. The high temperature environment will change the elastic modulus of the disc spring material, thereby affecting the stiffness and reset characteristics of the disc spring. At the same time, the rock fragments generated by the cutting are carried by the drilling fluid and impact the end face of the push mechanism's abutment column, forming an additional external constraint force. Moreover, this impact force is synchronous with the cutting heat—the more intense the cutting, the more heat is generated, and the more rock fragments are generated, and the greater the impact force. Therefore, the temperature rise and the increase in external constraint force are a coupled working condition that occurs simultaneously. It is necessary to simulate this thermo-mechanical coupling effect on the test bench in order to truly evaluate the performance of the push mechanism in the actual drilling process.

[0004] Current technologies lack a comprehensive verification test bench capable of simultaneously simulating pressure pulsations, dynamic temperature changes, and the coordinated changes in external constraint forces. Therefore, there is an urgent need for a dedicated verification test bench that can realistically simulate the aforementioned multi-factor coupled working conditions under laboratory conditions, providing reliable experimental data support for the engineering implementation of the target intelligent drill bit. Summary of the Invention

[0005] To address the technical problems in the prior art, this application provides a test bench and test method for verifying the flow-induced thrust characteristics of a drill bit vibration suppression and pushing mechanism.

[0006] This application provides a test bench and test method for verifying the flow-induced thrust characteristics of a drill bit vibration damping and pushing mechanism, which adopts the following technical solution: A test rig for verifying the flow-induced thrust characteristics of a drill bit vibration damping and pushing mechanism includes: Support frame, used to provide overall structural support; The push-back mechanism assembly, mounted on the support frame, includes a fixed platform, a simulated outer shell, a backing column, and a disc spring. The fixed platform is fixed to the support frame, and the simulated outer shell is mounted on the fixed platform. The simulated outer shell is a cylindrical structure with an inner cavity. The backing column is coaxially mounted in the inner cavity of the simulated outer shell, and an annular flow gap is formed between the backing column and the inner wall of the simulated outer shell. The backing column can be axially displaced upward under the pressure of the upward-flowing fluid in the flow gap. A baffle plate is fixed above the fixed platform, and a clearance hole for the backing column to pass through is opened in the center of the baffle plate. A water-blocking ring is provided circumferentially along the edge of the fixed platform, and a drainage hole is opened on the side wall of the water-blocking ring. The disc spring is installed between the backing column and the simulated outer shell and is used to provide an axial reset spring force to the backing column after the fluid pressure is removed, so that the backing column returns to its initial position. The fluid injection mechanism includes a water tank, a fluid injection connector, and a water pump. The fluid injection connector is located at the bottom of the simulated outer shell and is used to connect to the outlet of the water pump. The inlet of the water pump is connected to the water tank. The water pump pressurizes the fluid in the water tank and injects it into the inner cavity of the simulated outer shell. The fluid flows upward through the flow gap and generates an upward thrust on the abutment column. The fluid ejected upward from the flow gap is blocked by the baffle plate and falls onto the fixed platform, and then flows back to the water tank through the drain hole. The sensor assembly, mounted above the fixed platform, includes a thrust sensor and a displacement sensor. The thrust sensor is used to detect the magnitude of the axial thrust of the abutment column, and the displacement sensor is used to detect the amount of axial displacement of the abutment column. The data acquisition and processing system is electrically connected to the water pump and the sensor assembly. It is used to synchronously acquire the water pump output pressure, the thrust of the abutment column, and the displacement of the abutment column, and generate a multi-parameter characteristic curve of water pressure-displacement-thrust to verify the flow-induced thrust characteristics of the vibration damping actuator in the target smart drill bit.

[0007] A test method for a test bench for verifying the flow-induced thrust characteristics of a drill bit vibration damping and pushing mechanism, comprising the following steps: Step M1, parameter configuration: Based on the design working conditions of the target intelligent drill bit vibration damping actuator, select and match the corresponding specifications of the abutment column and disc spring, and install them in the push mechanism assembly; Step M2, baseline calibration: With the water pump off and no pressure in the cavity, record the zero-point readings of the displacement sensor and thrust sensor to complete the baseline calibration; Step M3, stepwise pressure test: Start the water pump and gradually increase the output water pressure of the water pump according to the preset pressure gradient. The pressure holding time of each pressure level shall not be less than 30 seconds. The data acquisition and processing system shall simultaneously record the current output water pressure of the water pump, the fluid pressure in the flow gap and the upward displacement of the abutment column. After reaching the rated pressure, the pressure shall be gradually reduced according to the same gradient, and the values ​​of each parameter during the pressure reduction process shall be recorded simultaneously. Step M4, Curve Generation and Analysis: Based on the collected data, generate the pump output water pressure-column displacement-column thrust characteristic curves for the entire process of pressurization and depressurization. Determine whether the curves fall within the water pressure-thrust-stroke parameter range specified in the design of the target intelligent drill bit. Compare the hysteresis difference between the pressurization curve and the depressurization curve to evaluate the disc spring reset performance, and perform linearity analysis on the characteristic curves. Step M5, parameter optimization iteration: If the verification results do not meet the design requirements, change the disc spring parameters or adjust the abutment column specifications, and repeat steps M1 to M4 until the optimal parameter combination that meets the design requirements is obtained.

[0008] In summary, this application includes at least one of the following beneficial technical effects: 1. By setting up replaceable support columns and disc springs, and using a data acquisition and processing system to simultaneously collect three parameters—pump output water pressure, support column thrust, and support column displacement—a multi-parameter characteristic curve of water pressure-displacement-thrust was generated. This enabled a systematic comparative verification of the flow-induced thrust characteristics under different annular flow gap sizes and disc spring elastic coefficient schemes, providing experimental data for the selection and finalization of key parameters of the target intelligent drill bit vibration suppression actuator.

[0009] 2. By setting a preload loading component, an adjustable axial preload can be applied to the upper end of the abutment column to simulate the external constraint force on the abutment column of the target intelligent drill bit under different geological conditions. The flow-induced thrust-displacement characteristic curve is obtained under the preload condition. Combined with the fluid temperature control module and the working condition linkage controller, the temperature change curve and the preload change curve are synchronously linked and controlled, so that the test bench can simulate the thermo-mechanical coupling working condition in which cutting heat conduction and rock cutting impact occur simultaneously. The obtained characteristic data is closer to the actual drilling environment than that under a single working condition.

[0010] 3. By using a series-connected pulsating pressure generation module, periodic pressure pulsations with adjustable frequency and amplitude are superimposed on the steady-state pressure output by the water pump. The data acquisition and processing system synchronously collects dynamic response data of pulsating pressure and displacement of the abutment column at a sampling rate of no less than ten times the pulsation frequency. The natural frequency and damping ratio of the disc spring-abutment column system are extracted through frequency domain analysis to determine whether the natural frequency of the system enters the pulsation frequency range of the mud pump, providing a quantitative basis for optimizing the disc spring parameters to avoid resonance risks. Attached Figure Description

[0011] Figure 1 This is a schematic diagram of the overall structure of the test bench for verifying the flow-induced thrust characteristics of the drill bit vibration suppression and pushing mechanism, provided in one embodiment of this application. Figure 2 yes Figure 1 Enlarged structural diagram at point A; Figure 3 This is a cross-sectional structural schematic diagram of a sensor assembly and a preload loading member provided in an embodiment of this application; Figure 4 This is a three-dimensional structural schematic diagram of a sensor assembly and a preload loading member provided in an embodiment of this application; Figure 5 This is a flowchart of the test method for a test bench for verifying the flow-induced thrust characteristics of a drill bit vibration suppression and pushing mechanism, provided in one embodiment of this application.

[0012] Explanation of reference numerals in the attached drawings: 100, Support frame; 200, Pushing mechanism assembly; 210, Fixed platform; 220, Simulated outer shell; 221, Limiting block; 230, Abutment post; 231, Guide hole; 240, Water baffle; 250, Water baffle ring; 251, Drain hole; 260, Guide post; 270, Disc spring; 271, Snap ring; 300, Fluid injection mechanism; 310, Water tank; 320, Fluid injection connector; 330, Water pump; 400... Sensor assembly; 410, thrust sensor; 420, displacement sensor; 421, connecting rod; 430, sensor mounting bracket; 440, column; 450, preload loading component; 451, preload sleeve; 452, pressure block; 453, preload spring; 454, preload block; 455, preload drive component; 500, pulsating pressure generating module; 600, fluid temperature control module; 610, temperature sensor; 620, heater; 630, cooler. Detailed Implementation

[0013] The technical solutions in the embodiments of the present invention will be further described in detail below with reference to the accompanying drawings. The described embodiments are only possible technical implementations of the present invention, but are not limited thereto. Other embodiments obtained by those skilled in the art in conjunction with the embodiments of the present invention without creative effort are also within the protection scope of the present invention.

[0014] This application mainly uses a water pump to simulate the drilling fluid pressure source to verify the flow-induced thrust characteristics of the push mechanism. This achieves the effect of verifying key parameters under multi-factor coupled working conditions, providing reliable data for the engineering of intelligent drill bits. The following is a further detailed description of this application.

[0015] Example 1 Please refer to Figure 1 and Figure 2 The test bench for verifying the flow-induced thrust characteristics of the vibration damping and pushing mechanism provided in this application includes a support frame 100, a pushing mechanism assembly 200, a fluid injection mechanism 300, a sensor assembly 400, and a data acquisition and processing system. The support frame 100 provides support for the overall structure. The pushing mechanism assembly 200 is mounted on the support frame 100 and integrates a disc spring 270. The fluid injection mechanism 300 injects pressurized fluid into the cavity of the simulated outer shell 220. The sensor assembly 400 detects the displacement of the abutment column 230 and the fluid pressure. The data acquisition and processing system simultaneously collects relevant parameters and generates multi-parameter characteristic curves, thereby realizing the verification of the flow-induced thrust characteristics of the vibration damping actuator in the target smart drill bit.

[0016] Specifically, the bottom of the support frame 100 is equipped with leveling pads, which can easily adjust the levelness of the support frame 100 and ensure the stability of the test bench.

[0017] In this embodiment, the support frame 100 serves as the structural foundation of the entire test bench, bearing the gravitational loads of various components such as the push-assist mechanism assembly 200 and the sensor assembly 400, as well as the reaction loads generated when the water pump 330 injects pressurized fluid during the test. The leveling feet can be adjusted in height by rotation during the installation and commissioning phase to keep the fixed platform 210 horizontal, thereby ensuring that the axis of the abutment column 230 is vertical. This prevents uneven wear or jamming between the abutment column 230 and the simulated outer shell 220 due to tilting, ensuring the accuracy of displacement measurement data. The open frame structure allows operators to access the push-assist mechanism assembly 200 from any direction, facilitating the replacement of components such as the abutment column 230 and disc springs, and also facilitating the connection and inspection of fluid pipelines, thus improving the convenience of the test operation.

[0018] Please refer to Figure 1 and Figure 2 The push-and-pull mechanism assembly 200 includes a fixed platform 210, a simulated outer shell 220, a push-and-pull column 230, a baffle plate 240, a baffle ring 250, a guide column 260, and a disc spring 270. The fixed platform 210 is fixed to the support frame 100. The simulated outer shell 220 is vertically mounted on the fixed platform 210 and is a cylindrical structure with an inner cavity, designed proportionally based on the structural dimensions of the guide perforation in the target intelligent drill bit. The push-and-pull column 230 is coaxially mounted within the inner cavity of the simulated outer shell 220, forming an annular flow gap with the inner wall of the simulated outer shell 220. Under the pressure of the upward-flowing fluid in the flow gap, the push-and-pull column 230 can be displaced axially upwards.

[0019] Please refer to Figure 2 The guide post 260 is fixed inside the simulated outer shell 220, and the abutment post 230 has an axially oriented guide hole 231, within which the guide post 260 is positioned. The guide post 260 guides and constrains the axial movement of the abutment post 230, ensuring that the abutment post 230 remains coaxial with the simulated outer shell 220 during upward displacement, preventing the abutment post 230 from deflecting or tilting and causing jamming, thus ensuring the accuracy of displacement measurement and the repeatability of the test.

[0020] Please refer to Figure 1 and Figure 2A baffle plate 240 is fixed above the fixed platform 210. The baffle plate 240 has a clearance hole in its center for the abutment column 230 to pass through. The inner diameter of the clearance hole is slightly larger than the outer diameter of the abutment column 230, allowing the abutment column 230 to move freely up and down within the clearance hole. A water-retaining ring 250 is provided circumferentially along the edge of the fixed platform 210, and a drain hole 251 is provided on the side wall of the water-retaining ring 250. Fluid sprayed upwards from the flow gap is blocked by the baffle plate 240 and flows onto the fixed platform 210. After being surrounded by the water-retaining ring 250, it flows back to the water storage tank 310 through the drain hole 251, achieving fluid recycling. The abutment column 230 can be made of different materials, such as stainless steel or alloy steel, as long as it can withstand the fluid pressure and meet the test requirements. The simulation outer shell 220 can also be manufactured using different processes, such as casting or forging, depending on the actual situation.

[0021] During the experiment, when the water pump 330 starts and injects pressurized fluid into the cavity of the simulated housing 220, the fluid first fills the bottom space of the simulated housing 220, and then flows upward through the annular flow gap between the abutment post 230 and the inner wall of the simulated housing 220. Since the cross-sectional area of ​​the annular flow gap is much smaller than the cross-sectional area of ​​the bottom of the cavity of the simulated housing 220, the fluid velocity increases and the pressure decreases as it passes through the gap. The pressure exerted by the fluid on the lower end face of the abutment post 230 is greater than the pressure exerted on the upper end face of the abutment post 230, thus creating an upward axial thrust difference, pushing the abutment post 230 upward against the elastic force of the disc spring 270. This process realistically simulates the physical process of drilling fluid in the target intelligent drill bit generating axial thrust when flowing through the annular gap between the abutment post and the inner wall of the guide perforation, causing the abutment post to extend. The baffle plate 240 and the baffle ring 250 allow for the orderly recovery of overflowing fluid, preventing fluid from splashing everywhere and affecting the normal operation of the sensor assembly 400, while also achieving fluid recycling and reducing the amount of water used in the experiment.

[0022] Please refer to Figure 2 The disc spring 270 is integrated inside the push mechanism assembly 200 and installed between the abutment post 230 and the simulated outer shell 220. When the water pump 330 stops supplying water and the internal fluid pressure is eliminated, the disc spring 270 pushes the abutment post 230 back to its initial position. The specifications of the disc spring can be changed according to actual needs to verify the influence of the disc spring parameters on the flow-induced thrust-displacement characteristics. In this embodiment, the lower end of the disc spring 270 is fixed to the abutment post 230 by a retaining ring 271, and the upper end of the disc spring 270 abuts against the limiting block 221 fixed inside the simulated outer shell 220. When the abutment post 230 moves upward, the lower end of the disc spring 270 moves upward, but the upper end of the disc spring 270 is blocked by the limiting block 221 and cannot move upward. Therefore, the disc spring 270 is compressed. When the upward thrust on the abutment post 230 decreases, the abutment post 230 returns to its original position under the action of the restoring force of the disc spring 270.

[0023] During the experiment, as the water pump 330 gradually increases its output water pressure, the upward thrust exerted by the fluid on the abutment column 230 gradually increases. The abutment column 230 overcomes the spring force and gradually moves upward, compressing the spring and storing elastic potential energy. When the water pump 330's output water pressure remains constant, the abutment column 230 remains stationary at the equilibrium position of the fluid thrust and the spring force. The displacement recorded by the displacement sensor 420 at this time is the steady-state displacement at that pressure level. When the water pump 330 gradually decreases its pressure or stops supplying water, the spring releases its elastic potential energy, pushing the abutment column 230 downward to reset. The replaceable design of the spring 270 allows a single test bench to perform system comparison verification of multiple spring parameter schemes, improving experimental efficiency and reducing engineering implementation risks.

[0024] Please refer to Figure 1 The fluid injection mechanism 300 includes a water storage tank 310, a fluid injection connector 320, and a water pump 330. The water storage tank 310 stores circulating fluid. The inlet of the water pump 330 is connected to the water storage tank 310, and the outlet of the water pump 330 is connected to the fluid injection connector 320 via a connecting pipe. The fluid injection connector 320 is located at the bottom of the simulation shell 220. The water pump 330 pressurizes the fluid in the water storage tank 310 and injects it into the inner cavity of the simulation shell 220. The pressurized fluid flows upward through the flow gap and exerts an upward thrust on the abutment column 230. The fluid ejected upward from the flow gap is blocked by the baffle plate 240 and falls onto the fixed platform 210, then flows back to the water storage tank 310 through the drain hole 251, forming a closed fluid circulation loop. The water pump 330 can be of different types, such as a centrifugal pump or a plunger pump, as long as it meets the pressure and flow requirements of the experiment. Pump 330 is a variable pressure pump with adjustable output pressure, covering the design working pressure range of the target smart drill bit to meet the requirements of step-by-step pressurization testing. Fluid injection connector 320 can be sealed to prevent fluid leakage.

[0025] During the test, water pump 330 draws and pressurizes fluid from water storage tank 310. The pressurized fluid is then transported through a connecting pipeline to fluid injection connector 320, and then enters the bottom cavity of the simulation housing 220. The output water pressure of water pump 330 can be controlled by adjusting the operating parameters of water pump 330, achieving continuous adjustment from zero to the rated operating pressure range. A sealed connection is used between fluid injection connector 320 and the output pipeline of water pump 330 to ensure no leakage occurs under high-pressure conditions.

[0026] Please refer to Figure 1The sensor assembly 400 includes a displacement sensor 420 and a thrust sensor 410. The displacement sensor 420 is used to detect the axial displacement of the abutment post 230, and its measuring end is in contact with the upper end of the abutment post 230 to acquire the displacement data of the abutment post 230 in real time. The thrust sensor 410 is used to detect the magnitude of the axial thrust of the abutment post 230.

[0027] During the experiment, the measuring end of the displacement sensor 420 remained in contact with the upper surface of the abutment column 230. When the abutment column 230 moved upward under the action of fluid thrust, the displacement sensor 420 detected and output a displacement signal in real time; when the abutment column 230 returned to its original position under the action of the disc spring, the displacement sensor 420 synchronously tracked and recorded the return process. The thrust sensor 410 was used to detect the magnitude of the axial thrust of the abutment column 230. The synchronous operation of the displacement sensor 420 and the thrust sensor 410 enabled the data acquisition and processing system to establish a precise correspondence between thrust and displacement, providing reliable raw data for generating characteristic curves.

[0028] The data acquisition and processing system is electrically connected to the water pump and the 330 sensor assembly (400Ω) to synchronously collect the water pump output pressure, the thrust of the abutment column, and the displacement of the abutment column. It generates a multi-parameter characteristic curve of water pressure-displacement-thrust to verify the flow-induced thrust characteristics of the vibration damping actuator in the target intelligent drill bit. The data acquisition and processing system can use a computer and relevant data acquisition software to process and analyze the acquired data.

[0029] The working process and technical effects of the data acquisition and processing system are as follows: The data acquisition and processing system is electrically connected to each sensor through a multi-channel data acquisition card. During the experiment, it synchronously acquires displacement signals from displacement sensor 420, thrust signals from thrust sensor 410, and output water pressure signals from water pump 330 at a set sampling rate. The acquired analog signals are converted by an A / D converter and stored in the computer. The data processing software filters, denoises, and calibrates the raw data, automatically generating water pump output water pressure-column displacement characteristic curves and fluid pressure-column displacement characteristic curves, which are displayed in real time on the display interface. Engineers can analyze these characteristic curves to determine whether the measured parameter scheme meets the design requirements of the target intelligent drill bit, thereby guiding the direction of parameter optimization. The multi-parameter synchronous acquisition method ensures strict correspondence of each parameter data on the time axis, avoids the timing deviation that may occur from multiple acquisitions, and improves the reliability of data analysis.

[0030] The complete working process of the entire device is as follows: First, based on the design conditions of the target intelligent drill bit vibration damping actuator, the operator selects and matches the corresponding specifications of the abutment post 230 and disc spring. The abutment post 230 is coaxially installed in the inner cavity of the simulated housing 220. The guide post 260 is inserted into the guide hole 231 of the abutment post 230 to achieve guiding engagement. The disc spring is installed between the abutment post 230 and the simulated housing 220. The fluid injection connector 320 is sealed and connected to the output pipeline of the water pump 330. The sensor assembly 400 is confirmed to be in centered contact with the upper end of the abutment post 230, thus completing the assembly of the test bench.

[0031] Then, with the water pump 330 not started, the zero-point readings of the displacement sensor 420 and the thrust sensor 410 are recorded to complete the baseline calibration.

[0032] Next, the water pump 330 is started. The water pump 330 draws fluid from the water storage tank 310 and pressurizes it. The pressurized fluid enters the bottom cavity of the simulated outer shell 220 through the connecting pipe and the fluid injection connector 320. After the fluid fills the bottom space of the cavity, it flows upward through the annular flow gap between the abutment post 230 and the inner wall of the simulated outer shell 220. When the fluid flows through the annular flow gap, it generates an upward axial thrust on the lower end face of the abutment post 230, pushing the abutment post 230 to overcome the return force of the disc spring and move upward. The abutment post 230 slides axially along the guide post 260, and the guide post 260 ensures the accuracy of the movement direction of the abutment post 230. The fluid flowing out of the annular flow gap is blocked by the baffle plate 240 and falls onto the fixed platform 210. After being surrounded by the baffle ring 250, it flows back to the water storage tank 310 through the drain hole 251, forming a closed fluid circulation loop.

[0033] During the upward displacement of the abutment column 230, the displacement sensor 420 detects the axial displacement of the abutment column 230 in real time, and the thrust sensor 410 detects the magnitude of the axial thrust of the abutment column 230. The data acquisition and processing system simultaneously collects data on three parameters: water pump output pressure, abutment column thrust, and abutment column displacement, and generates a multi-parameter characteristic curve of water pressure-displacement-pressure in real time, which is displayed on the computer screen.

[0034] The operator gradually increases the output water pressure of pump 330 according to the preset pressure gradient, maintaining the pressure at each level until the sensor reading stabilizes and then recording the data, until the rated working pressure is reached. Then, the pressure is gradually reduced according to the same gradient, with the values ​​of each parameter recorded simultaneously during the pressure reduction process. During the pressure reduction process, the spring force pushes the abutment column 230 to gradually return to its original position.

[0035] After the test, water pump 330 is stopped, and the retaining column 230 is fully reset to its initial position under the action of the disc spring. The data acquisition and processing system generates complete characteristic curves for the entire pressurization and depressurization process based on all acquired data, for engineers to analyze and evaluate. If the verification results do not meet the design requirements, the disc spring parameters are replaced or the retaining column 230 specifications are adjusted, and the above process is repeated until the optimal parameter combination that meets the design requirements is obtained.

[0036] The implementation principle of this embodiment is as follows: the test bench simulates the working process of the vibration damping actuator in the target intelligent drill bit through the coordinated work of its various components. The pressurized fluid injected by the water pump 330 flows in the annular flow gap, generating a thrust on the abutment column 230, causing it to move upwards. The cooperation between the guide column 260 and the guide hole 231 ensures the accuracy of the movement direction of the abutment column 230. The disc spring 270 integrated inside the push mechanism assembly 200 resets the abutment column 230 after the fluid pressure is removed. The baffle plate 240 and the baffle ring 250 achieve orderly recovery and recycling of the fluid. The sensor assembly 400 detects relevant parameters, and the data acquisition and processing system generates characteristic curves, providing reliable experimental data for the design and optimization of the target intelligent drill bit, and accurately verifying the flow-induced thrust characteristics of the vibration damping actuator.

[0037] Example 2 The difference between this embodiment and the above embodiment is that the width of the annular flow gap between the abutment post 230 and the inner wall of the simulated outer shell 220 is adjustable. By replacing the abutment post 230 with different outer diameter specifications, the flow area of ​​the annular flow gap is changed to simulate the flow-thrust relationship under different fitting clearance conditions in the target intelligent drill bit vibration damping actuator.

[0038] Specifically, the abutment post 230 can be designed with various outer diameter specifications and can be replaced as needed. When replacing the abutment post 230, simply remove the original abutment post 230 from the inner cavity of the simulation housing 220 and install the new abutment post 230. The new abutment post 230 also has a guide hole 231, which can cooperate with the guide post 260 for guidance. The annular flow gap formed between the abutment post 230 with different outer diameters and the inner wall of the simulation housing 220 is different, thus changing the flow area. The change in flow area affects the flow-thrust relationship of the fluid, affecting the magnitude of the axial thrust of the fluid on the abutment post 230. In this way, the flow-induced thrust characteristics under different gap size schemes can be systematically studied, providing more accurate parameter basis for the design of the target intelligent drill bit.

[0039] For example, you can prepare outer diameters of... Various specifications of abutment posts 230, when the inner diameter of the simulated outer shell 220 is fixed as At that time, the corresponding annular flow gap widths are respectively The smaller the gap, the greater the flow resistance when the fluid passes through, resulting in higher pressure on the lower end face of the abutment column 230 under the same pump output pressure, and a greater upward thrust, but a smaller flow rate. Conversely, the larger the gap, the smaller the flow resistance and the smaller the thrust, but the larger the flow rate. By comparing the water pressure-displacement characteristic curves under different gap widths, the optimal gap size that allows the abutment column 230 to achieve the target stroke within the design working pressure range can be found.

[0040] The implementation principle of this embodiment is as follows: the design of the replaceable abutment post 230 enables the test bench to simulate various different fitting clearance conditions, expanding the scope and flexibility of the test. Compared with test benches that can only fix one clearance size, this embodiment can more comprehensively study the flow-induced thrust characteristics, providing more data support for the optimized design of the target intelligent drill bit and reducing the risks of engineering implementation.

[0041] Example 3 Please refer to Figure 1 , Figure 3 and Figure 4 The difference between this embodiment and the above embodiment is that the sensor assembly 400 also includes a sensor fixing bracket 430, a column 440 and a preload loading member 450, which are used to apply an adjustable preload to the upper end of the abutment column 230 to simulate the external constraint force on the target smart drill bit against the abutment column 230 under different geological conditions, thereby measuring the flow-induced thrust-displacement characteristics under the applied preload condition.

[0042] Specifically, the sensor mounting bracket 430 is fixed above the mounting platform 210 via several columns 440, providing a stable mounting base for the sensor assembly 400 and ensuring that the axes of the sensor and the push mechanism assembly 200 are strictly aligned.

[0043] Please refer to Figure 3 and Figure 4The preload loading component 450 includes a preload sleeve 451, a pressure block 452, a preload spring 453, a preload block 454, and a preload drive component 455. The preload sleeve 451 is fixed above the fixed platform 210, and its axis is coaxial with the axis of the abutment post 230. The pressure block 452 is slidably disposed within the preload sleeve 451, with its lower end abutting against the upper end of the abutment post 230. When the abutment post 230 moves upward, the pressure block 452 slides upward accordingly. The preload block 454 is slidably disposed within the preload sleeve 451, located above the pressure block 452. The preload spring 453 is disposed within the preload sleeve 451, with its two ends connected to the pressure block 452 and the preload block 454, respectively. When the preload spring 453 is in a compressed state, it applies a downward elastic force to the pressure block 452, thereby applying a downward preload force to the abutment post 230 through the pressure block 452. One end of the pre-tightening drive 455 is connected to the pre-tightening sleeve 451, and the other end abuts against the pre-tightening block 454, used to adjust the position of the pre-tightening block 454 within the pre-tightening sleeve 451. When the pre-tightening drive 455 drives the pre-tightening block 454 downward, the pre-tightening spring 453 is further compressed, increasing the pre-tightening force applied to the pressure block 452 and the abutment post 230; when the pre-tightening drive 455 drives the pre-tightening block 454 upward, the compression of the pre-tightening spring 453 decreases, and the pre-tightening force decreases. By adjusting the pre-tightening drive 455, the magnitude of the pre-tightening force applied to the abutment post 230 can be precisely controlled.

[0044] Please refer to Figure 3The fixed end of the displacement sensor 420 is fixedly connected to the pre-tightening sleeve 451, and the movable end of the displacement sensor 420 is fixedly connected to the pressure block 452 via the connecting rod 421. In this embodiment, the displacement sensor 420 adopts a differential transformer type (LVDT) linear displacement sensor. Its fixed end (iron core coil assembly) is rigidly connected to the pre-tightening sleeve 451, so that the measurement reference is consistent with the entire sensor assembly 400; its movable end (iron core) is rigidly connected to the pressure block 452 via the connecting rod 421, and moves synchronously with the pressure block 452. When the fluid generates an upward thrust on the abutment column 230 and the upper end of the abutment column 230 pushes the pressure block 452 upward, the iron core moves upward synchronously with the connecting rod 421. The change in the axial position of the iron core in the coil causes a change in the difference in mutual inductance of the differential coil, which is converted into a voltage signal that is strictly linearly corresponding to the displacement by the signal conditioning circuit and output to the data acquisition and processing system. Since the fixed end reference point of the displacement sensor 420 (pre-tightening sleeve 451) and the starting point of movement of the abutment column 230 (the contact point between the pressure block 452 and the upper end of the abutment column 230) are both located in the rigid structural chain of the pre-tightening sleeve 451-fixed platform 210, common-mode errors such as bracket deformation are eliminated, ensuring the measurement accuracy of the axial displacement of the abutment column 230. At the same time, when the pre-tightening drive component 455 adjusts the position of the pre-tightening block 454 and changes the compression of the pre-tightening spring 453, the pressure block 452 is in a new equilibrium position under the combined action of the elastic force of the pre-tightening spring 453 and the reaction force of the abutment column 230. The connecting rod 421 moves accordingly, and the displacement sensor 420 synchronously outputs the updated displacement signal, ensuring accurate detection of the displacement of the abutment column 230 under the condition of applied pre-tightening force.

[0045] During the experiment, the preload loading component 450 applies a downward preload to the upper end of the abutment column 230. This preload is in the same direction as the spring force of the disc spring, jointly resisting the upward thrust generated by the fluid on the abutment column 230. Therefore, under the applied preload condition, the abutment column 230 requires a larger fluid thrust to produce the same displacement, i.e., the water pressure-displacement characteristic curve shifts towards the high pressure direction. By setting different preload values ​​(e.g., applying preloads of 0N, 50N, 100N, and 200N respectively), a family of water pressure-displacement characteristic curves under different preload conditions can be obtained, thereby establishing a three-parameter correlation model of preload-water pressure-abutment column displacement, providing data support for the parameter design of the vibration suppression actuator of the target intelligent drill bit under different geological conditions. In actual drilling, different types of formations exert different constraints on the abutment. For example, soft formations (such as mudstone) exert less constraint on the abutment, while hard formations (such as limestone and conglomerate) exert more constraint. The reaction force experienced by the abutment when it extends and abuts against the well wall is also different. The setting of the preload loading element 450 allows the test bench to simulate this difference, making the test results closer to the actual working conditions.

[0046] The implementation principle of this embodiment is as follows: the preload loading component 450, through the coordinated operation of the preload sleeve 451, pressure block 452, preload spring 453, preload block 454, and preload drive component 455, achieves the function of applying an adjustable preload to the abutment column 230, enabling the test bench to simulate the working conditions of the target intelligent drill bit under different geological conditions. By applying an adjustable preload, the influence of external constraint forces on the flow-induced thrust-displacement characteristics can be studied, providing a more accurate basis for the design and optimization of the target intelligent drill bit. Compared with test benches that do not consider external constraint forces, this embodiment can more comprehensively evaluate the performance of the vibration damping actuator, improving the reliability and applicability of the target intelligent drill bit.

[0047] Example 4 Please refer to Figure 1 The difference between this embodiment and the above embodiments is that it also includes a pulsating pressure generating module 500, which is connected in series in the pipeline between the water pump 330 and the fluid injection connector 320. The pulsating pressure generating module 500 can be a commercially available electro-hydraulic servo pulsating pressure generator. Its working principle is as follows: the pulsating pressure generator has an eccentric cam mechanism driven by a servo motor or a hydraulic cylinder controlled by an electro-hydraulic servo valve inside. The servo motor drives the eccentric cam to rotate or the hydraulic cylinder to reciprocate according to the frequency and amplitude parameters set by the controller, periodically changing the flow cross-sectional area of ​​the fluid in the pipeline or directly applying periodic volume disturbances to the fluid in the pipeline, thereby superimposing a periodic pressure pulsating signal with adjustable frequency and adjustable amplitude on the steady-state pressure output by the water pump 330. The operator sets the pulsation frequency (e.g., adjustable within the range of 1–50 Hz to cover the typical pump pulse pulsation frequency range of a three-cylinder mud pump in actual drilling) and the pulsation amplitude (e.g., adjustable within the range of 5%–30% of the steady-state pressure) through the control panel or host computer software of the pulsation pressure generator. The pulsation pressure generator then generates stable periodic pressure pulsations in the pipeline according to the set parameters. This pulsation pressure is superimposed on the steady-state pressure output by the water pump 330 and enters the inner cavity of the simulated housing 220 through the fluid injection connector 320. This causes the fluid pressure in the flow gap to exhibit a sinusoidal or approximately sinusoidal fluctuation with the steady-state pressure as the mean, the set amplitude as the amplitude, and the set frequency as the period, thereby simulating the pulsation characteristics of the mud pump output pressure in real drilling conditions.

[0048] The data acquisition and processing system synchronously acquires the dynamic response waveforms of pulsating pressure and the displacement of the abutment column at a high sampling rate (no less than ten times the pulsation frequency, for example, a sampling rate of no less than 100Hz when the pulsation frequency is 10Hz), generating dynamic flow-induced thrust-displacement frequency response characteristic curves. Analysis of these curves allows for the evaluation of the dynamic response characteristics of the disc spring-abutment column system under pulsating pressure, determining the presence of resonance risk, and providing crucial information for the optimized design of disc spring parameters.

[0049] The working process and technical effects of the pulsating pressure generation module 500 are as follows: During pulsating pressure testing, the water pump 330 is first started to establish a steady-state pressure in the pipeline. Then, the pulsating pressure generation module 500 is started to superimpose a pressure pulsation of one cycle onto the steady-state pressure. The operator can change the pulsation frequency and amplitude. In actual drilling, the output pressure of the three-cylinder mud pump exhibits periodic pulsations related to the pump stroke frequency. These pulsations may cause dynamic oscillations in the abutment column 230. If the natural frequency of the disc spring-abutment column system is close to the pump stroke pulsation frequency, resonance may occur, leading to an abnormal increase in the amplitude of the abutment column 230, affecting the vibration suppression effect and even causing the mechanism to fail. By simulating this pulsating condition on a test bench, resonance risks can be identified in advance during the design phase, and resonance can be avoided by adjusting the disc spring parameters, thereby improving the stability and reliability of the target intelligent drill bit.

[0050] The implementation principle of this embodiment is as follows: the pulsating pressure generation module 500 enables the test bench to simulate the pulsating characteristics of the mud pump output pressure under real drilling conditions. In actual drilling, the mud pump output pressure exhibits periodic pulsations, which may cause dynamic oscillations in the abutment column 230. By simulating this pulsating condition on the test bench, the dynamic response characteristics of the disc spring-abutment column system under pulsating pressure can be studied, avoiding resonance risks and improving the stability and reliability of the target intelligent drill bit. Compared with test benches that do not consider pressure pulsations, this embodiment can more realistically simulate actual working conditions, providing a more accurate basis for the design and optimization of the target intelligent drill bit.

[0051] Example 5 Please refer to Figure 1 and Figure 2 The difference between this embodiment and the above embodiments is that, based on embodiment 3, it also includes a fluid temperature control module 600 and a working condition linkage controller, which are used to realize the linkage control of temperature and preload, and simulate the coupled working condition where the cutting heat is conducted to the push mechanism when the drill bit cuts the rock, causing the temperature to rise, and at the same time the rock cuttings impact the push mechanism, causing the external constraint force to increase.

[0052] Please refer to Figure 2Specifically, the fluid temperature control module 600 includes a temperature sensor 610 disposed within the simulated housing 220, a heater 620 and a cooler 630 disposed at the fluid injection connector 320, and a temperature controller. The heater 620 can be an electric heating element to heat the fluid flowing through the fluid injection connector 320. The cooler 630 can be a plate heat exchanger or a cooling coil to cool the fluid using external cooling water. The temperature sensor 610 is disposed within the cavity of the simulated housing 220 to detect the fluid temperature in real time. The temperature controller receives the feedback signal from the temperature sensor 610, compares it with the set temperature value, and uses a PID control algorithm to control the operating states of the heater 620 and the cooler 630 respectively, precisely controlling the fluid temperature within the simulated housing 220 to the set value. The temperature control range covers ambient temperature (approximately 20°C) to simulated high-temperature downhole conditions (e.g., 120°C), with a temperature control accuracy of ±2°C.

[0053] The working condition linkage controller is connected to the fluid temperature control module 600 and the preload loading component 450 via signals. The working condition linkage controller contains a pre-stored drilling working condition linkage model. The design basis of this drilling working condition linkage model is as follows: During actual drilling, the drill bit generates a large amount of cutting heat when cutting rock. This cutting heat is conducted through the drill bit's metal structure to the area where the pusher mechanism is located, causing the temperature in that area to rise. Simultaneously, the rock fragments generated during cutting, carried by the drilling fluid, impact the end face of the pusher mechanism's abutment post, forming additional external constraint force. The more intense the cutting, the more heat is generated, the faster the temperature rises, and the more rock fragments are generated, resulting in a greater impact force on the abutment post. Therefore, the temperature rise and the increase in external constraint force occur synchronously in time.

[0054] Based on the above physical relationships, the drilling operation condition linkage model defines the temperature change curve. With preload variation curve The synchronous correspondence between them. For example, when the temperature changes from room temperature... Linearly increase to high temperature At that time, the preload force synchronously starts from zero. linearly increase to the maximum value When simulating a drilling stop condition, the temperature gradually decreases, and the preload also decreases accordingly.

[0055] According to the drilling working condition linkage model, the working condition linkage controller, through the control fluid temperature regulation module 600, keeps the fluid temperature along a preset temperature-time curve. While dynamically changing, the preload loading component 450 is synchronously controlled to ensure that the preload applied to the abutment post 230 follows the preload-time curve corresponding to temperature changes. Synchronous changes enable coordinated control of temperature and preload.

[0056] During the thermo-mechanical coupling test, the operator sets the parameters of the drilling condition linkage model (including temperature-time curves and preload-time curves) in the working condition linkage controller, and then starts the linkage test. The working condition linkage controller first sends a temperature setpoint command to the temperature controller, which then controls the heater 620 to start heating the fluid, gradually increasing the fluid temperature. Simultaneously, the working condition linkage controller sends a preload setpoint command to the preload loading component 450, which synchronously increases the preload applied to the abutment column 230. Throughout the entire process of temperature and preload linkage changes, the data acquisition and processing system synchronously collects five parameters: fluid temperature T, preload F, water pump output pressure P, fluid pressure p, and abutment column displacement ΔL. Through this linkage control method, the test bench can realistically simulate the coupled working condition of simultaneous heat conduction and cuttings impact when the drill bit cuts rock, making the test results closer to actual downhole working conditions. Compared to testing methods that fix the temperature or the preload separately, this linked simulation method can reveal the variation law of disc spring performance under the coupled effect of temperature and external constraint force, including the stiffness attenuation caused by the decrease in the elastic modulus of the disc spring material due to high temperature, and the compression effect of the increased preload on the displacement stroke of the abutment column, etc., providing more reliable data support for the parameter selection of the target intelligent drill bit under actual drilling conditions.

[0057] The implementation principle of this embodiment is as follows: through the coordinated operation of the fluid temperature control module 600 and the working condition linkage controller, the linkage control of temperature and preload is realized, realistically simulating the coupled working condition of cutting heat conduction and rock cutting impact occurring simultaneously when the drill bit cuts rock. The temperature is not constant, but dynamically changes according to a preset temperature-time curve, and the preload changes synchronously. This linkage simulation method can reveal the changing law of disc spring performance under the coupling effect of multiple factors, providing more comprehensive and reliable experimental data for the engineering implementation of the target intelligent drill bit.

[0058] Example 6 The difference between this embodiment and the above embodiments is that, based on embodiment 5, the drilling condition linkage model further includes multiple working condition profiles. Each working condition profile corresponds to the drilling conditions of the target smart drill bit in different well depths or different lithological formations. Each working condition profile is defined with corresponding temperature setting values, preload setting values, and water pump output water pressure setting values.

[0059] Specifically, for example, for a well designed to a depth of 3000m, the following working condition profile can be set: First working condition profile: well depth 0-1000m, soft mudstone formation, temperature setting 40℃, preload setting 30N, water pump output pressure setting 40% of rated pressure; Second working condition profile: well depth 1000-2000m, medium-hard sandstone formation, temperature setting 70℃, preload setting 80N, water pump output pressure setting 65% of rated pressure; The third working condition profile: well depth 2000-2500m, hard limestone formation, temperature setting 95℃, preload setting 150N, water pump output pressure setting 85% of rated pressure; Section 4 working condition profile: well depth 2500-3000m, carbonate rock formation containing flint interlayers, temperature setting 110℃, preload setting 200N, water pump output pressure setting 100% of rated pressure.

[0060] The operating condition linkage controller is also connected to the water pump 330 via a signal. Following a preset sequence of multiple operating condition profiles, it automatically switches between the temperature, preload, and water pressure parameter combinations corresponding to each profile. Within each operating condition profile, the controller controls the fluid temperature control module 600 to adjust the fluid temperature to the set value for that profile, controls the preload loading component 450 to adjust the preload to the set value for that profile, and controls the water pump 330 to adjust the output water pressure to the set value for that profile. After all parameters stabilize, the data acquisition and processing system performs a step-by-step pressurization test and collects data. After completing the test of one operating condition profile, the controller automatically switches to the next profile until all operating condition profile tests are completed.

[0061] The data acquisition and processing system collects the displacement data of the contact column under each working condition profile and automatically generates a family of flow-induced thrust-displacement characteristic curves for each well depth or lithological stratum condition, which are used by engineers to comprehensively analyze the applicability of the disc spring parameter scheme under the working conditions of the entire well section.

[0062] The working process and technical effects of automated sequence testing of multiple working condition profiles are as follows: Before the test begins, operators only need to input the parameters of each working condition profile into the working condition linkage controller. After starting the automated sequence test, the working condition linkage controller automatically executes the tests of each working condition profile in a preset order, without manual intervention. The test of each working condition profile includes steps such as parameter adjustment, stabilization waiting, step-by-step pressurization testing, and data acquisition, all of which are automatically completed by the working condition linkage controller and the data acquisition and processing system. This automated sequence testing method can complete system verification under multiple well depths or various lithological formations at once, significantly improving test efficiency, reducing human error, and ensuring the consistency and comparability of test conditions between different working condition profiles.

[0063] In this embodiment, through automated sequential testing of multiple working condition profiles, the test bench can systematically simulate the working conditions of the target intelligent drill bit under different working conditions throughout the well section, and obtain the flow-induced thrust-displacement characteristic data of the entire well section at one time, providing complete data support for the full-condition applicability evaluation of the disc spring parameter scheme.

[0064] Example 7 Please refer to Figure 3 and Figure 4 The difference between this embodiment and the previous embodiments is that, based on embodiment 5, the preload drive 455 specifically adopts a servo electric cylinder. The push rod of the servo electric cylinder is in coaxial contact with the preload block 454, and the working condition linkage controller realizes closed-loop precise control and real-time dynamic adjustment of the preload force through the servo electric cylinder.

[0065] Specifically, a servo electric cylinder is a precision linear actuator that integrates a servo motor and a ball screw, offering advantages such as high thrust accuracy, fast response speed, and programmable control. The servo electric cylinder's built-in force sensor detects the actual force applied to the preload block 454 by the push rod in real time. This force is transmitted to the abutment column 230 through the preload spring 453 and pressure block 452, forming the actual preload force, which is then fed back to the operating condition linkage controller. The operating condition linkage controller compares the actual preload force with the target preload force and adjusts the servo motor's speed and torque using a closed-loop PID control algorithm, ensuring that the actual preload force accurately tracks the target value, thus achieving closed-loop precise control of the preload force.

[0066] Under the control of the working condition linkage controller, the servo electric cylinder can achieve two modes in the preload-time curve: step change and continuous gradual change. The step change mode simulates the sudden increase in cuttings impact force when the drill bit encounters a hard interlayer (such as a flint layer or gravel layer)—in this case, the cutting heat also rises sharply due to increased cutting resistance, and both temperature and preload increase simultaneously. The continuous gradual change mode simulates the slow change in cuttings impact force with drilling depth when the drill bit is drilling steadily in a homogeneous formation—in this case, both temperature and preload show a slow and continuous change trend.

[0067] In this embodiment, in the step change mode, the working condition linkage controller sends a step command to the servo cylinder. The push rod of the servo cylinder drives the preload block 454 to move in a very short time (usually within milliseconds). The preload force is increased from the current value to the target value through the preload spring 453 and the pressure block 452, simulating the transient process of a sudden increase in rock cutting impact force when the drill bit suddenly encounters a hard interlayer. At this time, the data acquisition and processing system records the displacement response of the abutment column 230 under the condition of sudden change in preload force at a high sampling rate, which can evaluate the transient response characteristics of the disc spring-abutment column system under sudden load. In the continuous gradual change mode, the working condition linkage controller sends a continuously changing command to the servo cylinder. The push rod of the servo cylinder smoothly adjusts the position of the preload block 454 according to the preset preload force-time curve. The preload force is smoothly adjusted through the preload spring 453 and the pressure block 452, simulating the process of slow change in rock cutting impact force when the drill bit is drilling steadily in a homogeneous formation. Compared to simple manual adjustment, servo electric cylinders have advantages such as high control precision, fast response speed, and the ability to track complex preload curves, which can more realistically simulate the dynamic changes of external constraint forces during actual drilling.

[0068] In this embodiment, by using a servo electric cylinder as the pre-tightening drive component 455 and combining it with the closed-loop control of the working condition linkage controller, high precision, fast response, and programmable dynamic adjustment of the pre-tightening force are achieved. This enables the test bench to accurately simulate various external constraint force change modes encountered by the drill bit under different geological conditions, including two typical working conditions: abrupt change and gradual change. This provides more accurate data support for the parameter design of the target intelligent drill bit under complex geological conditions.

[0069] Example 8 Please refer to Figure 5 The test method of the drill bit vibration damping and pushing mechanism flow-induced thrust characteristic verification test bench provided in this application embodiment adopts the drill bit vibration damping and pushing mechanism flow-induced thrust characteristic verification test bench as described in any one of Embodiments 1 to 7, and includes the following steps: Step M1, Parameter Configuration: Based on the design conditions of the vibration damping actuator of the target intelligent drill bit, select and match the corresponding specifications of the abutment post 230 and disc spring, and install them in the push mechanism assembly 200. This step requires selecting a suitable outer diameter abutment post 230 (to determine the flow area of ​​the annular flow gap) and a disc spring with a suitable elastic coefficient according to the design requirements of the target intelligent drill bit to ensure that the test can accurately simulate the working conditions of the target intelligent drill bit. Seal the connection between the fluid injection connector 320 and the output pipeline of the water pump 330, and confirm that the sensor assembly 400 is aligned and in contact with the upper end of the abutment post 230 to complete the assembly and connection of the test bench.

[0070] Step M2, Baseline Calibration: With the water pump 330 off, record the zero-point readings of the displacement sensor 420 and the thrust sensor 410 to complete the baseline calibration. This step is to ensure the accuracy of subsequent measurement data and eliminate initial sensor errors.

[0071] Step M3, stepwise pressurization test: Start water pump 330 and gradually increase the pump output water pressure according to the preset pressure gradient. The pressure gradient step size should not exceed 10% of the rated working pressure, with a total of no less than 5 gradient levels. The pressure holding time for each pressure level should not be less than 30 seconds. After the sensor readings stabilize, the data acquisition and processing system simultaneously records the current water pump output water pressure value P, the fluid pressure value p in the flow gap, and the upward displacement ΔL of the abutment column. After reaching the rated pressure, the pressure is gradually reduced according to the same gradient, and the values ​​of each parameter are recorded simultaneously during the pressure reduction process. Through stepwise pressurization and depressurization tests, the displacement response of the abutment column 230 under different pressures can be obtained, and the flow-induced thrust-displacement characteristics can be studied.

[0072] Step M4, Curve Generation and Analysis: Based on the collected data, generate a characteristic curve of pump output water pressure P-impact column displacement ΔL-impact column thrust throughout the entire pressurization and depressurization process. Determine whether the curve falls within the water pressure-thrust-stroke parameter range specified in the target intelligent drill bit design, and compare the hysteresis difference between the pressurization curve and the depressurization curve. To evaluate the disc spring's reset performance and perform linearity analysis on the characteristic curves, this step assesses whether the linear relationship between the displacement of the abutment column and the water pressure within the design working pressure range meets the linearity design requirements of the target intelligent drill bit's push response. This step helps evaluate whether the performance of the vibration damping actuator meets the design requirements, providing a basis for subsequent parameter optimization.

[0073] Step M5, parameter optimization iteration: If the verification results do not meet the design requirements, change the disc spring parameters or adjust the 230 specification of the abutment post according to the direction of deviation, and repeat steps M1 to M4 until the optimal parameter combination that meets the design requirements is obtained, providing a basis for the final design of the vibration damping actuator of the target intelligent drill bit. Through continuous iterative optimization, the most suitable parameter combination for the target intelligent drill bit can be found, improving the performance of the vibration damping actuator.

[0074] Step M6, Thermo-Mechanical Coupling Test: Activate the fluid temperature control module 600 and the working condition linkage controller, and according to the pre-stored drilling working condition linkage model, make the fluid temperature follow the preset temperature-time curve. The dynamic raising simulates the process of heat generation from drill bit cutting being transferred to the pushing mechanism, while the preload loading element 450 follows a preload-time curve that corresponds to temperature changes. The preload is increased synchronously to simulate the process of rock cutting impact force increasing synchronously with cutting heat. Throughout the entire process of temperature and preload changes in tandem, the data acquisition and processing system simultaneously collects five parameters: fluid temperature T, preload F, water pump output pressure P, fluid pressure p, and abutment displacement ΔL. Based on the collected five parameters, a flow-induced thrust-displacement characteristic curve under temperature-preload linkage conditions is generated and compared with the characteristic curve under normal temperature and zero preload conditions in step M3. The combined effect of the coupling effect of temperature increase and preload increase on the abutment displacement response is analyzed, and the performance degradation degree of the disc spring under thermo-mechanical coupling conditions is evaluated. This step can simulate the thermo-mechanical coupling conditions of the drill bit in actual operation and study the influence of temperature and preload on the performance of the vibration damping actuator. Specific analysis includes: evaluating the degree of stiffness degradation of the disc spring due to the decrease in the material's elastic modulus under high temperature conditions; evaluating the compression effect of increased preload on the abutment displacement stroke; and evaluating the change in the disc spring's reset hysteresis characteristics under the coupling effect of temperature and preload.

[0075] Step M7, Dynamic Test of Pulsating-Thermo-Mechanical Coupling: Based on the thermo-mechanical coupling test in Step M6, the pulsating pressure generation module 500 is simultaneously activated, superimposing periodic pressure pulsations of a set frequency and amplitude onto the steady-state pressure output by the water pump 330. Under the simultaneous action of temperature, preload, and pressure pulsations, the data acquisition and processing system synchronously acquires the pulsating pressure waveform, the dynamic response waveform of the abutment column displacement, the dynamic response waveform of the abutment column thrust, fluid temperature, and preload data at a high sampling rate (not less than ten times the pulsation frequency). Frequency domain analysis (e.g., Fast Fourier Transform FFT) is performed on the acquired pulsating pressure, abutment column thrust, and displacement response data to extract the natural frequencies of the disc spring-abutment column system under the current temperature and preload conditions. Damping ratio The natural frequencies were extracted at different temperature-preload linkage stages (e.g., low temperature and low preload stage, medium temperature and medium preload stage, and high temperature and high preload stage). Damping ratio A model was established to investigate the drift law of the natural frequency as a function of temperature and preload. This step determines whether the system's natural frequency falls within the mud pump pulsation frequency range of the target smart drill bit's actual operating conditions, thus posing a resonance risk. Based on this, the disc spring parameters are optimized to ensure that the system's natural frequency avoids the mud pump pulsation frequency range throughout the entire operating range. This step comprehensively evaluates the performance of the vibration damping actuator under multi-factor coupled conditions, providing a more accurate basis for the design and optimization of the target smart drill bit. If a resonance risk exists in a certain operating condition, the disc spring parameters (changing the stiffness) or the mass of the abutment column 230 is adjusted to ensure that the system's natural frequency avoids the mud pump pulsation frequency range throughout the entire operating range, and the test is repeated for verification.

[0076] The implementation principle of this embodiment is as follows: This experimental method comprehensively and systematically verifies the flow-induced thrust characteristics of the drill bit vibration damping and pushing mechanism through a series of steps. From parameter configuration to step-by-step pressurization testing, and then to thermo-mechanical coupling linkage testing and pulsating-thermal-mechanical three-factor coupled dynamic testing, it can simulate various working conditions of the target intelligent drill bit in actual operation and study the influence of multiple factors on the performance of the vibration damping actuator. Through the analysis and processing of the collected data, relevant characteristic curves and drift law models are established, providing a reliable basis for the design and optimization of the target intelligent drill bit. Compared with traditional experimental methods, this method more comprehensively and accurately evaluates the performance of the vibration damping actuator, improving the reliability and applicability of the target intelligent drill bit.

[0077] The specific embodiments described above do not constitute a limitation on the scope of protection of this application. Any other corresponding changes and modifications made based on the technical concept of this application should be included within the scope of protection of this application.

Claims

1. A test bench for verifying the flow-induced thrust characteristics of a drill bit vibration suppression and pushing mechanism, characterized in that, include: Support frame, used to provide overall structural support; The push-back mechanism assembly, installed on the support frame, includes a fixed platform, a simulated outer shell, a backing column, and a disc spring. The fixed platform is fixed to the support frame, and the simulated outer shell is installed on the fixed platform. The simulated outer shell is a cylindrical structure with an inner cavity. The backing column is coaxially installed in the inner cavity of the simulated outer shell, and an annular flow gap is formed between the backing column and the inner wall of the simulated outer shell. The backing column can be axially displaced upward under the pressure of the upward-flowing fluid in the flow gap. A baffle plate is fixed above the fixed platform, and a clearance hole for the backing column to pass through is opened in the center of the baffle plate. A water-blocking ring is provided circumferentially along the edge of the fixed platform, and a drainage hole is opened on the side wall of the water-blocking ring. The disc spring is installed between the backing column and the simulated outer shell and is used to provide an axial reset spring force to the backing column after the fluid pressure is removed, so that the backing column returns to its initial position. The fluid injection mechanism includes a water tank, a fluid injection connector, and a water pump. The fluid injection connector is located at the bottom of the simulated outer shell and is used to connect to the outlet of the water pump. The inlet of the water pump is connected to the water tank. The water pump pressurizes the fluid in the water tank and injects it into the inner cavity of the simulated outer shell. The fluid flows upward through the flow gap and generates an upward thrust on the abutment column. The fluid ejected upward from the flow gap is blocked by the baffle plate and falls onto the fixed platform, and then flows back to the water tank through the drain hole. The sensor assembly, mounted above the fixed platform, includes a thrust sensor and a displacement sensor. The thrust sensor is used to detect the magnitude of the axial thrust of the abutment column, and the displacement sensor is used to detect the amount of axial displacement of the abutment column. The data acquisition and processing system is electrically connected to the water pump and the sensor assembly. It is used to synchronously acquire the water pump output pressure, the thrust of the abutment column, and the displacement of the abutment column, and generate a multi-parameter characteristic curve of water pressure-displacement-thrust to verify the flow-induced thrust characteristics of the vibration damping actuator in the target smart drill bit.

2. The test rig for verifying the flow-induced thrust characteristics of the drill bit vibration suppression and pushing mechanism according to claim 1, characterized in that, The width of the annular flow gap between the abutment post and the inner wall of the simulated outer shell is adjustable. By replacing the abutment posts with different outer diameter specifications, the flow area of ​​the annular flow gap is changed to simulate the flow-thrust relationship under different fitting clearance conditions in the target intelligent drill bit vibration damping actuator.

3. The test rig for verifying the flow-induced thrust characteristics of the drill bit vibration suppression and pushing mechanism according to claim 1, characterized in that, The sensor assembly further includes a sensor mounting bracket, columns, and a preload loading component. The sensor mounting bracket is fixed above the fixed platform via several columns. The preload loading component includes a preload sleeve, a pressure block, a preload spring, a preload block, and a preload drive component. The preload sleeve is fixed above the fixed platform. The pressure block is slidably disposed within the preload sleeve, with its lower end abutting against the upper end of the abutment column. The preload block is slidably disposed within the preload sleeve. The preload spring is disposed within the preload sleeve, with its two ends respectively contacting the pressure block and the abutment column. The pre-tightening block is connected, with one end of the pre-tightening drive member connected to the pre-tightening sleeve and the other end abutting against the pre-tightening block, used to adjust the position of the pre-tightening block within the pre-tightening sleeve. The pre-tightening force loading member is used to apply an adjustable pre-tightening force to the upper end of the abutment column to simulate the external constraint force experienced by the target smart drill bit against the abutment column under different geological conditions, thereby measuring the flow-induced thrust-displacement characteristics under the applied pre-tightening force condition. The fixed end of the displacement sensor is fixedly connected to the pre-tightening sleeve, and the movable end of the displacement sensor is fixedly connected to the pressure block via a connecting rod.

4. The test rig for verifying the flow-induced thrust characteristics of the drill bit vibration suppression and pushing mechanism according to claim 1, characterized in that, It also includes a pulsating pressure generation module, which is connected in series in the pipeline between the water pump and the fluid injection joint. This module is used to superimpose periodic pressure pulsations with adjustable frequency and amplitude on the steady-state pressure output by the water pump to simulate the pulsating characteristics of the mud pump output pressure in real drilling conditions. The data acquisition and processing system synchronously acquires dynamic response data of pulsating pressure and displacement of the contact column at a sampling rate of not less than ten times the pulsating frequency, and generates a dynamic flow-induced thrust-displacement frequency response characteristic curve.

5. The test bench for verifying the flow-induced thrust characteristics of the drill bit vibration suppression and pushing mechanism according to claim 3, characterized in that, It also includes a fluid temperature control module and a working condition linkage controller; The fluid temperature control module includes a temperature sensor disposed inside the simulated housing, a heater and a cooler disposed at the fluid injection connector, and a temperature controller. The temperature controller controls the working state of the heater and cooler according to the feedback signal of the temperature sensor to regulate the fluid temperature inside the simulated housing to a set value. The working condition linkage controller is connected to the fluid temperature control module and the preload loading component respectively. The working condition linkage controller has a pre-stored drilling working condition linkage model. The drilling working condition linkage model defines the synchronous correspondence between the temperature change curve and the preload change curve. It is used to simulate the coupled working condition where the cutting heat is conducted to the push mechanism when the drill bit cuts the rock, causing the temperature to rise, and at the same time the rock cuttings impact the push mechanism, causing the external constraint force to increase. According to the drilling working condition linkage model, the working condition linkage controller controls the fluid temperature regulation module to dynamically change the fluid temperature along the preset temperature-time curve, and simultaneously controls the preload loading component to make the preload applied to the abutment column change synchronously according to the preload-time curve corresponding to the temperature change, thereby realizing the linkage regulation of temperature and preload.

6. The test bench for verifying the flow-induced thrust characteristics of the drill bit vibration suppression and pushing mechanism according to claim 5, characterized in that, The drilling condition linkage model includes multiple condition profiles. Each condition profile corresponds to the drilling conditions of the target smart drill bit in different well depths or different lithological formations. Each condition profile is defined with corresponding temperature setpoints, preload setpoints, and water pump output pressure setpoints. The working condition linkage controller is also connected to the water pump signal. According to the preset order of the multiple working condition profiles, it automatically switches the temperature, preload and water pressure parameter combinations corresponding to each working condition profile. The data acquisition and processing system collects the displacement data of the abutment column under each working condition profile and automatically generates a family of flow-induced thrust-displacement characteristic curves under each well depth or lithological stratum condition.

7. The test rig for verifying the flow-induced thrust characteristics of the drill bit vibration suppression and pushing mechanism according to claim 5, characterized in that, The preload drive is a servo electric cylinder, and the push rod of the servo electric cylinder is in coaxial contact with the preload block. The working condition linkage controller realizes closed-loop precise control and real-time dynamic adjustment of the preload force through the servo electric cylinder. Under the control of the working condition linkage controller, the servo electric cylinder can realize two modes in the preload-time curve: step change and continuous gradual change. The step change mode is used to simulate the working condition where the rock cutting impact force suddenly increases when the drill bit encounters a hard interlayer. The continuous gradual change mode is used to simulate the working condition where the rock cutting impact force changes slowly with the drilling depth when the drill bit is drilling steadily in a homogeneous stratum.

8. A test method for a test bench for verifying the flow-induced thrust characteristics of a drill bit vibration damping and pushing mechanism, characterized in that, The test bench for verifying the flow-induced thrust characteristics of the drill bit vibration suppression and pushing mechanism as described in any one of claims 1 to 7 includes the following steps: Step M1, parameter configuration: Based on the design working conditions of the target intelligent drill bit vibration damping actuator, select and match the corresponding specifications of the abutment column and disc spring, and install them in the push mechanism assembly; Step M2, baseline calibration: With the water pump off and no pressure in the cavity, record the zero-point readings of the displacement sensor and thrust sensor to complete the baseline calibration; Step M3, stepwise pressure test: Start the water pump and gradually increase the output water pressure of the water pump according to the preset pressure gradient. The pressure holding time of each pressure level shall not be less than 30 seconds. The data acquisition and processing system shall simultaneously record the current output water pressure of the water pump, the fluid pressure in the flow gap and the upward displacement of the abutment column. After reaching the rated pressure, the pressure shall be gradually reduced according to the same gradient, and the values ​​of each parameter during the pressure reduction process shall be recorded simultaneously. Step M4, Curve Generation and Analysis: Based on the collected data, generate the pump output water pressure-column displacement-column thrust characteristic curves for the entire process of pressurization and depressurization. Determine whether the curves fall within the water pressure-thrust-stroke parameter range specified in the design of the target intelligent drill bit. Compare the hysteresis difference between the pressurization curve and the depressurization curve to evaluate the disc spring reset performance, and perform linearity analysis on the characteristic curves. Step M5, parameter optimization iteration: If the verification results do not meet the design requirements, change the disc spring parameters or adjust the abutment column specifications, and repeat steps M1 to M4 until the optimal parameter combination that meets the design requirements is obtained.

9. The test method according to claim 8, characterized in that, It also includes step M6, thermo-mechanical coupling linkage test: The fluid temperature control module and the working condition linkage controller are activated. According to the pre-stored drilling working condition linkage model, the fluid temperature is dynamically increased along the preset temperature-time curve to simulate the process of heat generation from drill bit cutting being transmitted to the pushing mechanism. At the same time, the preload loading component increases the preload according to the preload-time curve corresponding to the temperature change to simulate the process of rock cutting impact force increasing synchronously with cutting heat. Throughout the entire process of temperature and preload changes, the data acquisition and processing system simultaneously collects five parameters: fluid temperature, preload, pump output water pressure, fluid pressure, and displacement of the abutment column. Based on the collected five-parameter data, a flow-induced thrust-displacement characteristic curve under temperature-preload linkage conditions is generated and compared with the characteristic curve under normal temperature and zero preload conditions in step M3. The combined effect of the coupling effect of temperature increase and preload increase on the displacement response of the abutment column is analyzed, and the performance degradation degree of the disc spring under thermo-mechanical coupling conditions is evaluated.

10. The test method according to claim 9, characterized in that, It also includes step M7, dynamic testing of the coupling of three factors: pulsation, heat, and force. Based on the thermo-mechanical coupling test in step M6, the pulsating pressure generation module is simultaneously activated to superimpose periodic pressure pulsations of a set frequency and amplitude onto the steady-state pressure output by the water pump. Under the simultaneous influence of three factors—temperature, preload, and pressure pulsation—the data acquisition and processing system synchronously acquires pulsating pressure waveforms, dynamic response waveforms of the abutment column displacement, dynamic response waveforms of the abutment column thrust, fluid temperature, and preload data. Frequency domain analysis was performed on the collected pulsating pressure, abutment thrust, and displacement response data to extract the natural frequency and damping ratio of the disc spring-abutment system under the current temperature and preload conditions. The natural frequency and damping ratio were extracted at different temperature-preload linkage stages. A drift law model of the natural frequency with temperature and preload was established to determine whether the system natural frequency enters the mud pump pulsation frequency range in the actual working condition of the target smart drill bit and generates resonance risk in each working condition stage. Based on this, the disc spring parameters were optimized to ensure that the system natural frequency avoids the mud pump pulsation frequency range in the entire working condition range.

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