Pipeline flow metering device

Abstract

The invention discloses a pipeline flow metering device, and belongs to the technical field of flow meters. A pipeline flow metering device comprises a measuring pipe body, a front flow guide assembly, a turbine measuring assembly and a rear flow guide assembly are arranged in the measuring pipe body, the rear flow guide assembly is of a damping grid structure formed by perforated plates, and the two ends of the turbine measuring assembly are connected with the front flow guide assembly and the rear flow guide assembly respectively. According to the pipeline flow metering device, the shaft-mounted vibrator and the rotor built-in vibrator are integrated, dirt on the turbine rotor and the turbine shaft can be automatically removed under the condition that the pipeline flow metering device is not detached, the maintenance frequency and the maintenance cost are reduced, the working temperature of the magnetostriction rods and the magnetostriction laminations is effectively reduced by adopting the water-cooled jackets and the heat dissipation fins, and the working efficiency of the magnetostriction rods and the magnetostriction laminations is improved. The stability and reliability of the system are improved, and the service life is prolonged.

Description

Technical Field

[0001] The present invention relates to the technical field of flow meters, in particular to a pipeline flow metering device. Background Art

[0002] In the field of fluid measurement, turbine flowmeters are widely used due to their high precision, good repeatability, and wide applicability. However, a major problem facing traditional turbine flowmeters is the accumulation of dirt on the turbine rotor and turbine shaft, which increases measurement errors and requires regular maintenance and cleaning. Furthermore, traditional cleaning methods often rely on mechanical or chemical cleaning, which is not only time-consuming and labor-intensive, but can also damage the equipment. Therefore, the development of a turbine flowmeter that can self-clean and maintain long-term stability has become a key demand within the industry. Summary of the Invention

[0003] The object of the present invention is to provide a pipeline flow metering device. By integrating a shaft-mounted vibrator and a rotor-built-in vibrator, the pipeline flow metering device can automatically clean dirt on the turbine rotor and turbine shaft without disassembly, thereby reducing maintenance frequency and cost and solving the problems raised in the above-mentioned background technology.

[0004] To achieve the above-mentioned objectives, the present invention provides the following technical solutions: a pipeline flow metering device, comprising a measuring tube body, wherein a front flow guide assembly, a turbine measuring assembly and a rear flow guide assembly are arranged inside the measuring tube body, the rear flow guide assembly is a rectifier grid structure composed of a porous plate, the two ends of the turbine measuring assembly are respectively connected to the front flow guide assembly and the rear flow guide assembly, the front flow guide assembly is installed at the inlet end of the measuring tube body, and an intelligent sensor module is integrated on the measuring tube body.

[0005] Preferably, the turbine measurement assembly includes a turbine rotor and a turbine shaft, and the two ends of the turbine shaft are respectively connected to the front guide assembly and the rear guide assembly to support the position of the turbine rotor. A shaft-mounted vibrator is provided on the turbine shaft, and a rotor-built-in vibrator is provided in the turbine rotor. The turbine rotor is driven to vibrate by the shaft-mounted vibrator and the rotor-built-in vibrator, which plays a self-cleaning role. The outer ring of the turbine rotor is provided with blades, and the blades are embedded with neodymium magnets. The Hall sensor is used to detect and identify the rotation speed of the turbine rotor and calculate the flow rate of the fluid.

[0006] Preferably, the shaft-mounted vibrator includes a magnetostrictive rod, a drive coil, a water cooling jacket and a bias magnetic ring. The drive coil is coaxially sleeved on the outside of the magnetostrictive rod, and the water cooling jacket is sleeved on the outside of the drive coil. The water cooling jacket is provided with a spiral groove. The spiral groove design on the water cooling jacket increases the flow path of the coolant and improves the heat dissipation efficiency. The bias magnetic ring is provided at the end of the water cooling jacket, and the bias magnetic ring is interference-connected to the inner wall of the turbine shaft.

[0007] Preferably, a vibration isolation ring is sleeved on the end of the turbine shaft, and the turbine shaft is connected to the front guide assembly and the rear guide assembly respectively through the vibration isolation ring. The ring can effectively block the transmission of mechanical vibration to the front guide assembly and the rear guide assembly, avoiding them from resonating with the turbine shaft, thereby protecting the stability and reliability of the entire system.

[0008] Preferably, both ends of the turbine shaft are conical structures, which play a guiding role. A connecting short shaft is provided at the connection between the turbine shaft and the turbine rotor. The connecting short shaft is connected to the turbine shaft through a bearing, and the contact surface between the connecting short shaft and the bearing is provided with a spiral guide groove. The spiral pitch of the spiral guide groove close to the front guide component end is smaller than the spiral pitch of the spiral guide groove close to the rear guide component end. The dense spiral grooves at the front end improve the scouring of the bearing wall by the fluid and avoid dirt deposition on the inner wall of the bearing. The loose spiral grooves at the rear end are more conducive to dirt discharge, and the spiral guide grooves include deep grooves and shallow grooves arranged in parallel. The deep grooves are used to increase the scouring force, and the shallow grooves facilitate dirt discharge and prevent deposition. When the fluid passes through the deep and shallow spiral guide grooves, it generates a heavy and light impact force on the inner wall of the bearing, like a wave, which is conducive to improving the self-cleaning ability of the bearing.

[0009] Preferably, the rotor built-in vibrator includes a shell, a receiving coil, a magnetostrictive lamination, a heat dissipation fin and a mass balance cavity. The shell is made of titanium alloy material, and the receiving coil is laser welded inside the shell. The inner ring of the receiving coil is provided with a magnetostrictive lamination. The receiving coil and the magnetostrictive lamination are vacuum-sealed. The inner side of the magnetostrictive lamination is provided with a heat dissipation fin, and the heat dissipation fins are distributed around the mass balance cavity. The heat dissipation fins are copper-diamond composite fins and adopt a microneedle array.

[0010] Preferably, the front guide assembly includes a guide cone and guide vanes. The guide vanes are arranged at equal intervals around the guide cone, and the ends of the guide vanes are fixedly connected to the inner wall of the measuring tube.

[0011] Preferably, the intelligent sensor module includes a Hall sensor to detect the rotation speed of the turbine rotor;

[0012] Vibration monitoring sensor to detect the vibration status of the turbine rotor;

[0013] Temperature sensor: The temperature sensor adopts a plug-in structure to monitor the fluid temperature;

[0014] Pressure sensor, measuring the pressure of the measuring tube;

[0015] The signal processing unit integrates AI algorithms to process the signals received by the sensor, including flow calculation and vibration compensation calculation. The vibration monitoring sensor detects the vibration state of the turbine rotor. The frequency analysis module of the signal processing unit extracts the vibration characteristics and combines them with the adaptively filtered flow signal. The intelligent signal compensation algorithm is used for calculation and finally corrects and outputs the final flow value.

[0016] Wireless communication module, used for transmitting data.

[0017] Preferably, the Hall sensor senses the magnetic field changes of the neodymium magnet as the turbine rotor rotates. The Hall sensor is electrically connected to the signal processing unit, converts each induced magnetic field change into an electrical pulse signal, and transmits the electrical pulse signal to the signal processing unit. The signal processing unit calculates the speed of the turbine rotor and obtains the flow rate of the fluid. The signal processing unit specifically includes:

[0018] The signal acquisition submodule is used to receive the electric pulse signal transmitted by the Hall sensor, amplify the electric pulse signal, and perform signal shaping processing to obtain the target electric pulse signal;

[0019] The counting submodule counts the target electrical pulse signal within a preset time length to obtain pulse data;

[0020] The analysis submodule obtains the pulse data within a preset time length and calculates the turbine rotor speed using the following formula:

[0021]

[0022] Wherein, ω is the rotation speed, N is the number of pulses, m is the number of neodymium magnets, and t is the preset time;

[0023] Calculate the flow velocity v of the pipeline fluid based on the rotational speed of the turbine rotor:

[0024]

[0025] Where v is the flow velocity of the pipeline fluid, S is the cross-sectional area of ​​the pipeline, and δ is the instrument factor of the pipeline flowmeter;

[0026] The fluid flow rate is then obtained by multiplying the fluid flow rate by the cross-sectional area of ​​the pipe.

[0027] Preferably, the electric pulse signal shaping process includes removing noise interference from the electric pulse signal and compensating for deviations caused by turbine rotor vibration, specifically including:

[0028] The electric pulse signal transmitted by the Hall sensor is subjected to a first filtering process by a first filter to filter out noise and unnecessary frequency components, and the electric pulse signal with an amplitude that is too high or too low is removed by a limiting circuit to obtain a preliminary electric pulse signal;

[0029] Acquire the real-time vibration parameters of the turbine rotor, including amplitude and vibration frequency, based on the vibration monitoring sensor, and record the time value of the real-time vibration parameters of the turbine rotor, taking each acquisition time as a sampling point to form a continuous sampling interval;

[0030] Screening the amplitude and / or vibration frequency of the turbine rotor within the sampling interval, wherein the amplitude and / or vibration frequency exceed the preset amplitude threshold and the preset vibration frequency, and recording the corresponding time value as the abnormality collection time;

[0031] Acquiring a preliminary electrical pulse signal detected at the abnormality acquisition moment, and performing a second filtering process on the preliminary electrical pulse signal through a second filter, wherein the second filter adaptively adjusts a filter coefficient through an adaptive filtering algorithm to minimize an output error;

[0032] The preliminary electric pulse signal is subjected to a second filtering process by a second filter to form a compensation electric pulse signal;

[0033] The compensation electric pulse signal and the remaining preliminary electric pulse signals except the sampling interval are recombined in chronological order to form a target electric pulse signal.

[0034] Compared with the prior art, the present invention has the following beneficial effects:

[0035] A pipeline flow metering device of the present invention integrates a shaft-mounted vibrator and a rotor-built vibrator. The pipeline flow metering device can automatically remove dirt from the turbine rotor and turbine shaft without disassembly, thereby reducing maintenance frequency and cost. The water cooling jacket and heat dissipation fins are used to effectively reduce the operating temperature of the magnetostrictive rods and magnetostrictive laminations, improve the stability and reliability of the system, and extend the service life. The design of the guide component ensures the stability of the fluid before entering the turbine rotor and reduces the impact of turbulence on measurement. The design of the spiral guide groove enhances the self-cleaning ability of the bearing and prevents performance degradation caused by dirt deposition. The Hall sensor detects the rotational speed of the turbine rotor and can accurately calculate the fluid flow rate by combining the data of the temperature sensor and the pressure sensor. The signal processing unit integrates an AI algorithm and realizes intelligent compensation of the flow value through analysis of the vibration state and adaptive filtering of the flow signal, thereby further improving the measurement accuracy. BRIEF DESCRIPTION OF THE DRAWINGS

[0036] Figure 1 This is a structural diagram of the pipeline flow metering device of the present invention;

[0037] Figure 2 This is an exploded view of the front guide assembly, turbine measurement assembly, and rear guide assembly of the present invention;

[0038] Figure 3 It is a front view of the turbine shaft of the present invention;

[0039] Figure 4 A sectional view of a turbine shaft portion of the present invention;

[0040] Figure 5 This is a cross-sectional view of the turbine rotor of the present invention.

[0041] In the figure: 1. Measuring tube body; 2. Front guide assembly; 21. Guide cone; 22. Guide vane; 3. Turbine measurement assembly; 31. Turbine rotor; 311. Casing; 312. Receiving coil; 313. Magnetostrictive laminations; 314. Heat dissipation fins; 315. Mass balance chamber; 316. Blades; 32. Turbine shaft; 321. Magnetostrictive rod; 322. Drive coil; 323. Water cooling jacket; 324. Bias magnetic ring; 325. Vibration isolation ring; 326. Connecting short shaft; 3261. Spiral guide groove; 4. Rear guide assembly; 5. Intelligent sensor module. DETAILED DESCRIPTION

[0042] The following will clearly and completely describe the technical solutions in the embodiments of the present invention in conjunction with the accompanying drawings. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without making creative efforts are within the scope of protection of the present invention.

[0043] A major problem faced by conventional turbine flowmeters is the accumulation of dirt on the turbine rotor and turbine shaft, which can lead to increased measurement errors and require regular maintenance and cleaning. Furthermore, conventional cleaning methods often rely on mechanical or chemical cleaning, which are not only time-consuming and labor-intensive but can also damage the equipment. Figure 1-Figure 5 , this embodiment provides the following technical solutions:

[0044] A pipeline flow metering device includes a measuring tube body 1, in which a front flow guide component 2, a turbine measurement component 3 and a rear flow guide component 4 are arranged. The two ends of the turbine measurement component 3 are respectively connected to the front flow guide component 2 and the rear flow guide component 4. The front flow guide component 2 is installed at the inlet end of the measuring tube body 1, and an intelligent sensor module 5 is integrated on the measuring tube body 1.

[0045] Specifically, the turbine measurement assembly 3 includes a turbine rotor 31 and a turbine shaft 32. The two ends of the turbine shaft 32 are respectively connected to the front guide assembly 2 and the rear guide assembly 4 to support the position of the turbine rotor 31. An axially mounted vibrator is provided on the turbine shaft 32. A cavity is opened in the turbine rotor 31, and a rotor-built-in vibrator is provided in the cavity. The turbine rotor 31 is driven to vibrate by the axially mounted vibrator and the rotor-built-in vibrator to prevent dirt from accumulating on the turbine rotor 31 and the turbine shaft 32, thereby playing a self-cleaning role.

[0046] More specifically, the axially mounted vibrator includes a magnetostrictive rod 321, a drive coil 322, a water-cooling jacket 323, and a biasing magnetic ring 324. The drive coil 322 is coaxially sleeved on the exterior of the magnetostrictive rod 321. The magnetostrictive rod 321 and the drive coil 322 utilize a non-contact gap fit, with a gap distance of 0.15±0.02 mm and filled with thermally conductive silicone grease. The drive coil 322 is constructed from alumina ceramic. When the system is activated, an alternating current is applied to the drive coil 322. This current generates a varying magnetic field around the drive coil 322. Due to the non-contact gap fit between the magnetostrictive rod 321 and the drive coil 322, and the thermally conductive silicone grease filling to improve heat conduction efficiency, the magnetostrictive rod 321 undergoes periodic expansion and contraction deformation due to the magnetostrictive effect. This deformation is caused by the rearrangement of magnetic domains within the material under the influence of the applied magnetic field, resulting in dimensional changes. The drive coil 322 is externally sheathed with a water cooling jacket 323, which is provided with a spiral groove. The magnetostrictive rod 321 generates heat during operation. This heat is transferred to the drive coil 322 through thermal grease and further conducted to the externally sheathed water cooling jacket 323 through the alumina ceramic frame. The spiral groove design on the water cooling jacket 323 increases the flow path of the coolant, improves the heat dissipation efficiency, and effectively reduces the operating temperature of the entire device. A bias magnetic ring 324 is provided at the end of the water cooling jacket 323. The bias magnetic ring 324 is interference-connected with the inner wall of the turbine shaft 32. The shaft-mounted vibrator excites axial ultrasonic vibration, which is transmitted to the turbine hub and causes microscopic displacement of the blade roots of the turbine rotor 31, destroying the adhesion of contaminants and achieving self-cleaning. The bias magnetic ring 324 is set at the end of the water cooling jacket 323. It is interference-connected with the inner wall of the turbine shaft 32, providing a stable bias magnetic field environment for the magnetostrictive rod 321, helping to optimize the working performance of the magnetostrictive rod 321 and maintaining efficient telescopic response over a wider range. In addition, a vibration isolation ring 325 is sleeved on the end of the turbine shaft 32, and the turbine shaft 32 is connected to the front guide assembly 2 and the rear guide assembly 4 respectively through the vibration isolation ring 325. In order to prevent the vibration of the turbine shaft 32 from affecting the front guide assembly 2 and the rear guide assembly 4, a vibration isolation ring 325 is provided at the end of the turbine shaft 32. The ring can effectively block the transmission of mechanical vibration to the front guide assembly 2 and the rear guide assembly 4, avoiding them from resonating with the turbine shaft 32, thereby protecting the stability and reliability of the entire system.

[0047] The frequency of the shaft-mounted vibrator is selected to be 25-30kHz, the amplitude is controlled to be <50μm, the working mode is intermittent, and the cleaning cycle duty cycle is <15%. The shaft-mounted vibrator mainly cleans the turbine rotor 31 and the root of the blade 316.

[0048] Both ends of the turbine shaft 32 are conical structures, which play a guiding role. At the same time, a connecting short shaft 326 is provided at the connection between the turbine shaft 32 and the turbine rotor 31. The connecting short shaft 326 is connected to the turbine shaft 32 through a bearing, and the contact surface between the connecting short shaft 326 and the bearing is provided with a spiral guide groove 3261. The spiral pitch of the spiral guide groove 3261 near the front guide component 2 is smaller than the spiral pitch of the spiral guide groove 3261 near the rear guide component 4. The dense spiral grooves at the front end improve the scouring of the bearing wall by the fluid and avoid dirt deposition on the inner wall of the bearing. The loose spiral grooves at the rear end are more conducive to dirt discharge. The spiral guide groove 3261 includes deep grooves and shallow grooves arranged in parallel. The deep groove is used to increase the scouring force, and the shallow groove facilitates dirt discharge and prevents deposition. When the fluid passes through the deep and shallow spiral guide grooves 3261, it produces a heavy and light impact force on the inner wall of the bearing, like a wave, which is conducive to improving the self-cleaning ability of the bearing. It should be noted that a μ-metal double-layer shield is provided inside the connecting short shaft 326 , which can attenuate 90% of the stray magnetic field outside the axial vibrator and reduce the influence of the external magnetic field on the axial vibrator.

[0049] The rotor's built-in vibrator includes a housing 311, a receiving coil 312, magnetostrictive laminations 313, cooling fins 314, and a mass balance cavity 315. The housing 311 is made of titanium alloy and has a permalloy lining for magnetic field shielding. The receiving coil 312 is laser-welded within the housing 311. The inner ring of the receiving coil 312 is provided with magnetostrictive laminations 313. The receiving coil 312 and the magnetostrictive laminations 313 are vacuum-sealed. Cooling fins 314 are provided on the inner side of the magnetostrictive laminations 313 and are distributed around the mass balance cavity 315. The cooling fins 314 are copper-diamond composite fins made of a microneedle array with a height of 0.3 mm and a spacing of 0.5 mm.

[0050] The frequency of the rotor's built-in vibrator is selected to be 50-60kHz, and the amplitude is controlled to be <30μm. Such high-frequency vibration can more effectively cause micro-displacement, which helps to break the adhesion of more stubborn or fine particles of pollutants. It is particularly suitable for cleaning the entire blade 316. The lower amplitude can reduce the mechanical stress on the equipment while still being sufficient to produce enough micro-displacement to achieve a cleaning effect.

[0051] When the system is started, an alternating current is passed through the receiving coil 312. This current generates a varying magnetic field around the receiving coil 312. As the alternating magnetic field generated by the receiving coil 312 changes, the magnetostrictive laminations 313 undergo periodic expansion and contraction deformation due to the magnetostrictive effect. This deformation is caused by the rearrangement of magnetic domains within the material under the influence of the external magnetic field, resulting in dimensional changes. The expansion and contraction movement of the magnetostrictive laminations 313 is converted into mechanical vibrations. These vibrations can be directly transmitted within the turbine rotor 31, thereby achieving micro-displacement excitation of the turbine rotor 31 and its attachments. Such vibrations help to destroy the attachment points of contaminants, achieving a self-cleaning effect. The mass balance cavity 315 is provided to compensate for the unbalanced weight of components such as the magnetostrictive laminations 313 and the heat dissipation fins 314, ensuring the stability of the entire turbine rotor 31 during high-speed rotation.

[0052] The outer ring of the turbine rotor 31 is provided with a blade 316 , and the blade 316 is embedded with a neodymium magnet. The rotation speed of the turbine rotor 31 is detected by a Hall sensor to calculate the flow rate of the fluid.

[0053] The front guide assembly 2 includes a guide cone 21 and guide vanes 22. The guide vanes 22 are arranged at equal distances around the guide cone 21. The ends of the guide vanes 22 are fixedly connected to the inner wall of the measuring tube body 1. The rear guide assembly 4 is a rectifying grid structure composed of a porous plate.

[0054] The intelligent sensor module 5 includes a Hall sensor for detecting the rotational speed of the turbine rotor 31. The Hall sensor is opposite to the installation position of the neodymium magnet and is arranged circumferentially along the inner wall of the measuring tube body 1; a vibration monitoring sensor, which is installed on the bearing connecting the turbine rotor 31 and the turbine shaft 32 to detect the vibration state of the turbine rotor 31; a temperature sensor, which adopts an inserted structure to monitor the fluid temperature; a pressure sensor, which is installed on the inner wall of the measuring tube body 1 to measure the pressure of the measuring tube body 1; a signal processing unit, which integrates an AI algorithm to process the signals received by the sensor, including flow calculation and vibration compensation calculation. The vibration monitoring sensor detects the vibration state of the turbine rotor 31, extracts the vibration characteristics through the frequency analysis module of the signal processing unit, and combines the adaptively filtered flow signal with the intelligent signal compensation algorithm for calculation, and finally corrects and outputs the final flow value; and a wireless communication module for transmitting data.

[0055] Preferably, the Hall sensor senses the magnetic field changes of the neodymium magnet as the turbine rotor 31 rotates. The Hall sensor is electrically connected to the signal processing unit, converts each induced magnetic field change into an electrical pulse signal, and transmits the electrical pulse signal to the signal processing unit. The signal processing unit calculates the rotational speed of the turbine rotor 31 and obtains the flow rate of the fluid. The signal processing unit specifically includes:

[0056] The signal acquisition submodule is used to receive the electric pulse signal transmitted by the Hall sensor, amplify the electric pulse signal, and perform signal shaping processing to obtain the target electric pulse signal;

[0057] The counting submodule counts the target electrical pulse signal within a preset time length to obtain pulse data;

[0058] The analysis submodule obtains pulse data within a preset time length and calculates the speed of the turbine rotor 31 using the following formula:

[0059]

[0060] Wherein, ω is the rotation speed, N is the number of pulses, m is the number of neodymium magnets, and t is the preset time;

[0061] The flow velocity v of the pipeline fluid is calculated based on the rotation speed of the turbine rotor 31:

[0062]

[0063] Where v is the flow velocity of the pipeline fluid, S is the cross-sectional area of ​​the pipeline, and δ is the instrument factor of the pipeline flowmeter;

[0064] The fluid flow rate is then obtained by multiplying the fluid flow rate by the cross-sectional area of ​​the pipe.

[0065] The principle and effect of the above technical solution are: the Hall sensor is used to sense the changes in the magnetic field of the neodymium magnet in real time as the turbine rotor 31 rotates, and the electric pulse signal is collected. The electric pulse signal is amplified and shaped to reduce the influence of interference factors such as noise and vibration on the signal, and a target electric pulse signal that can be used for analysis is obtained. The rotational speed of the turbine rotor 31 is calculated based on the target electric pulse signal, and the flow velocity v of the pipeline fluid is calculated based on the rotational speed of the turbine rotor 31, and then the flow rate of the fluid is obtained. The calculation method is stable and reliable.

[0066] Preferably, the electric pulse signal shaping process includes removing noise interference from the electric pulse signal and compensating for deviations caused by vibration of the turbine rotor 31, specifically including:

[0067] The electric pulse signal transmitted by the Hall sensor is subjected to a first filtering process by a first filter to filter out noise and unnecessary frequency components, and the electric pulse signal with an amplitude that is too high or too low is removed by a limiting circuit to obtain a preliminary electric pulse signal;

[0068] Acquire real-time vibration parameters of the turbine rotor 31, including amplitude and vibration frequency, based on the vibration monitoring sensor, and record the time value of acquiring the real-time vibration parameters of the turbine rotor 31, with each acquisition time being regarded as a sampling point to form a continuous sampling interval;

[0069] Within the sampling interval, the amplitude and / or vibration frequency of the turbine rotor 31 exceeding the preset amplitude threshold and the preset vibration frequency are screened and the corresponding time value is recorded as the abnormality collection time;

[0070] A preliminary electric pulse signal detected at the abnormal acquisition moment is obtained, and the preliminary electric pulse signal is subjected to a second filtering process through a second filter. The second filter adaptively adjusts the filter coefficient through an adaptive filtering algorithm to minimize the output error. The adaptive filtering algorithm adopts the LMS algorithm. For the input preliminary electric pulse signal, the formula for the output compensation electric pulse signal after the second filtering process is:

[0071]

[0072] Among them, y(n) is the compensation electric pulse signal output by the second filter at time n, w i (n) is the tap coefficient of the ith filter at the nth moment, x(n) is the preliminary electrical pulse signal input, x(ni) is the preliminary electrical pulse signal input at the nith moment, N is the filter order, and the filter order reflects the complexity of the filter structure, usually referring to the power of the highest-order term in the transfer function, or the number of energy storage elements in the circuit, which can be determined according to actual selection;

[0073] Adaptively adjusting filter coefficients by an adaptive filtering algorithm includes calculating an error;

[0074] f(n)=m(n)-y(n), where m(n) is the expected electrical pulse signal at time n; f(n) is the error value of the electrical pulse signal;

[0075] When the error value of the electric pulse signal at the nth moment is detected, the updated filter tap coefficient is calculated by the following formula: w(n+1)=w(n)+2uf(n), w(n) is the filter tap coefficient at the nth moment, w(n+1) is the filter tap coefficient at the n+1th moment, where u is the step size parameter, and the value range of u is (0.001~0.01);

[0076] The preliminary electric pulse signal is subjected to a second filtering process by a second filter to form a compensation electric pulse signal;

[0077] The compensation electric pulse signal and the remaining preliminary electric pulse signals excluding the sampling interval are recombined in chronological order to form a target electric pulse signal.

[0078] The principle and effect of the above technical solution are as follows: the present invention performs a first filtering process by using a first filter, which can perform a preliminary screening and filtering of all collected electric pulse signals to obtain preliminary electric pulse signals. At the same time, since the vibration of the turbine rotor 31 may cause errors in the collected signals, the electric pulse signals collected at the vibration moment are then processed for a second time by using a second filter. Specifically, the filter coefficients are adaptively adjusted through an adaptive filtering algorithm to reduce the errors.

[0079] Since the filter tap coefficient determines the frequency response of the filter, its value range will affect the stability and filtering effect of the filter, and will also affect the phase characteristics. If the tap coefficient is set properly, it can effectively pass the frequency components of the signal and suppress the frequency components of noise and interference signals, thereby improving the reliability and accuracy of the detection results. If the tap coefficient is too large or too small, it will cause the filter to diverge or the bracelet to be slow, thereby affecting the stability and accuracy of the detection results. Therefore, adaptively adjusting the filter tap coefficient can reduce the output error and improve the detection accuracy. The present invention combines the compensated electric pulse signal after the second filtering process and the remaining preliminary electric pulse signals except the sampling interval to form a target electric pulse signal, which can improve the accuracy and reliability of the target electric pulse signal. Only when the target electric pulse signal is accurate and reliable, the pipeline flow value calculated by the target electric pulse signal is accurate. Therefore, the processing process of the target electric pulse signal is of great significance for improving the flow calculation result of the present invention.

[0080] It should be noted that in order to ensure accurate flow measurement, it is usually necessary to select a Hall sensor that is suitable for the working environment. The temperature sensor and pressure sensor detect the ambient temperature and pressure. In extreme environments, the Hall sensor can be stopped from working.

[0081] Working process: The fluid enters from the inlet of the measuring tube body 1, is rectified by the guide cone 21 and the adjustable guide vane 22 of the front guide assembly 2, and forms a stable laminar flow. The fluid impacts the blades 316 of the turbine rotor 31, driving it to rotate. The speed is proportional to the flow rate. The driving coil 322 is fed with 25-30kHz AC, which excites the magnetostrictive rod 321 to generate axial ultrasonic vibration. The vibration is transmitted to the turbine rotor 31 through the turbine shaft 32, destroying the dirt attached to the root of the impeller 316. The water cooling jacket 323 circulates coolant through the spiral groove. The receiving coil 312 receives high-frequency electrical energy and drives the magnetostrictive laminate 313 to generate radial micro- Vibration, with an amplitude of 0.5-3μm, directly acts on the tip and trailing edge of the impeller 316 to remove micro-particle contaminants. The heat dissipation of the heat dissipation fin 314 is enhanced by the microneedle array. The neodymium magnet embedded in the impeller 316 periodically triggers the Hall sensor and outputs a pulse signal. The vibration sensor at the bearing collects acceleration data and identifies abnormal spectra. The temperature / pressure sensor corrects the influence of fluid density in real time. The signal processing unit separates vibration interference through the LSTM algorithm and outputs the compensated flow value. The wireless communication module supports remote diagnosis. The spiral guide groove 3261 continuously flushes the bearing. Combined with the intermittent vibration mode, zero-maintenance operation is achieved.

[0082] It should be noted that, in this document, relational terms such as first and second, etc., are used only to distinguish one entity or operation from another entity or operation, and do not necessarily require or imply any actual relationship or order between these entities or operations. Moreover, the terms "comprises," "comprising," or any other variations thereof are intended to cover non-exclusive inclusion, such that a process, method, article, or apparatus that includes a list of elements includes not only those elements but also other elements not explicitly listed, or elements inherent to such process, method, article, or apparatus.

[0083] While the embodiments of the present invention have been shown and described, it will be apparent to those skilled in the art that various changes, modifications, substitutions, and alterations can be made to the embodiments without departing from the principles and spirit of the invention.

Claims

1. A pipeline flow metering device, comprising a measuring tube body (1), characterized in that: The measuring tube body (1) is provided with a front flow guide component (2), a turbine measuring component (3) and a rear flow guide component (4), the two ends of the turbine measuring component (3) are respectively connected to the front flow guide component (2) and the rear flow guide component (4), the front flow guide component (2) is installed at the inlet end of the measuring tube body (1), and an intelligent sensor module (5) is integrated on the measuring tube body (1), which detects the turbine speed and calculates the flow rate through a Hall sensor, performs vibration compensation in combination with a vibration monitoring sensor, and uses an adaptive filtering algorithm to correct the flow signal, and finally outputs an accurate flow value, and is equipped with a wireless communication module to transmit data.

2. The pipeline flow metering device according to claim 1, characterized in that: The turbine measurement assembly (3) comprises a turbine rotor (31) and a turbine shaft (32), wherein two ends of the turbine shaft (32) are respectively connected to a front guide assembly (2) and a rear guide assembly (4), a shaft-mounted vibrator is provided on the turbine shaft (32), a rotor built-in vibrator is provided inside the turbine rotor (31), and a blade (316) is provided on the outer ring of the turbine rotor (31), and a neodymium magnet is embedded in the blade (316).

3. The pipeline flow metering device according to claim 2, characterized in that: The shaft-mounted vibrator comprises a magnetostrictive rod (321), a driving coil (322), a water cooling jacket (323) and a bias magnetic ring (324); the driving coil (322) is coaxially sleeved on the outside of the magnetostrictive rod (321); the water cooling jacket (323) is sleeved on the outside of the driving coil (322); the bias magnetic ring (324) is provided at the end of the water cooling jacket (323); and the bias magnetic ring (324) is interference-connected to the inner wall of the turbine shaft (32).

4. The pipeline flow metering device according to claim 3, characterized in that: A vibration isolation ring (325) is sleeved on the end of the turbine shaft (32), and the turbine shaft (32) is connected to the front flow guide assembly (2) and the rear flow guide assembly (4) respectively through the vibration isolation ring (325).

5. The pipeline flow metering device according to claim 2, characterized in that: A connecting stub shaft (326) is provided at the connection between the turbine shaft (32) and the turbine rotor (31), the connecting stub shaft (326) being connected to the turbine shaft (32) via a bearing, and a spiral guide groove (3261) is provided on the contact surface between the connecting stub shaft (326) and the bearing, the spiral pitch of the spiral guide groove (3261) close to one end of the front guide assembly (2) being smaller than the spiral pitch of the spiral guide groove (3261) close to one end of the rear guide assembly (4), and the spiral guide groove (3261) comprises a deep groove and a shallow groove arranged in parallel.

6. The pipeline flow metering device according to claim 2, characterized in that: The rotor built-in vibrator comprises a housing (311), a receiving coil (312), a magnetostrictive lamination (313), a heat dissipation fin (314) and a mass balance cavity (315); the housing (311) is made of a titanium alloy material, and the receiving coil (312) is welded inside the housing (311) by laser; the inner ring of the receiving coil (312) is provided with a magnetostrictive lamination (313); the receiving coil (312) and the magnetostrictive lamination (313) are sealed by vacuum potting; the inner side of the magnetostrictive lamination (313) is provided with a heat dissipation fin (314), and the heat dissipation fin (314) is distributed around the mass balance cavity (315).

7. The pipeline flow metering device according to claim 6, characterized in that: The front flow guide assembly (2) comprises a flow guide cone (21) and flow guide vanes (22). The flow guide vanes (22) are arranged at equal intervals around the flow guide cone (21), and the ends of the flow guide vanes (22) are fixedly connected to the inner wall of the measuring tube body (1).

8. The pipeline flow metering device according to claim 2, characterized in that: The intelligent sensor module (5) includes a Hall sensor for detecting the rotation speed of the turbine rotor (31); A vibration monitoring sensor for detecting a vibration state of the turbine rotor (31); Temperature sensor: The temperature sensor adopts a plug-in structure to monitor the fluid temperature; A pressure sensor for measuring the pressure of the measuring tube (1); The signal processing unit integrates an AI algorithm and processes the signal received by the sensor, including flow calculation and vibration compensation calculation. The vibration monitoring sensor detects the vibration state of the turbine rotor (31), extracts the vibration characteristics through the frequency analysis module of the signal processing unit, and combines the adaptively filtered flow signal with the intelligent signal compensation algorithm for calculation, and finally corrects and outputs the final flow value; Wireless communication module, used for transmitting data.

9. The pipeline flow metering device according to claim 8, characterized in that: The Hall sensor senses the magnetic field change of the neodymium magnet as the turbine rotor (31) rotates. The Hall sensor is electrically connected to the signal processing unit, converts each induced magnetic field change into an electric pulse signal, and transmits the electric pulse signal to the signal processing unit. The signal processing unit calculates the rotation speed of the turbine rotor (31) and obtains the flow rate of the fluid. The signal processing unit specifically includes: The signal acquisition submodule is used to receive the electric pulse signal transmitted by the Hall sensor, amplify the electric pulse signal, and perform signal shaping processing to obtain the target electric pulse signal; The counting submodule counts the target electrical pulse signal within a preset time length to obtain pulse data; The analysis submodule obtains pulse data within a preset time length and calculates the rotation speed of the turbine rotor (31) using the following formula: Wherein, ω is the rotation speed, N is the number of pulses, m is the number of neodymium magnets, and t is the preset time; The flow velocity v of the pipeline fluid is calculated based on the rotation speed of the turbine rotor (31): Where v is the flow velocity of the pipeline fluid, S is the cross-sectional area of ​​the pipeline, and δ is the instrument factor of the pipeline flowmeter; The fluid flow rate is then obtained by multiplying the fluid flow rate by the cross-sectional area of ​​the pipe.

10. The pipeline flow metering device according to claim 9, characterized in that: The electric pulse signal shaping process includes removing noise interference from the electric pulse signal and compensating for deviations caused by vibration of the turbine rotor (31), specifically including: The electric pulse signal transmitted by the Hall sensor is subjected to a first filtering process by a first filter to filter out noise and unnecessary frequency components, and the electric pulse signal with an amplitude that is too high or too low is removed by a limiting circuit to obtain a preliminary electric pulse signal; Acquiring real-time vibration parameters of the turbine rotor (31), including amplitude and vibration frequency, based on a vibration monitoring sensor, and recording the time value of acquiring the real-time vibration parameters of the turbine rotor (31), taking each acquisition time as a sampling point to form a continuous sampling interval; Screening the amplitude and / or vibration frequency of the turbine rotor (31) that exceeds a preset amplitude threshold and a preset vibration frequency within the sampling interval, and recording the corresponding time value as the abnormality collection time; Acquiring a preliminary electrical pulse signal detected at the abnormality acquisition moment, and performing a second filtering process on the preliminary electrical pulse signal through a second filter, wherein the second filter adaptively adjusts a filter coefficient through an adaptive filtering algorithm to minimize an output error; The preliminary electric pulse signal is subjected to a second filtering process by a second filter to form a compensation electric pulse signal; The compensation electric pulse signal and the remaining preliminary electric pulse signals except the sampling interval are recombined in chronological order to form a target electric pulse signal.

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