A flow meter sensor

Abstract

This application discloses a flow meter sensor, relating to the field of sensor technology, and aims to solve the problem of how to improve the accuracy of flow meter sensors in detecting fluid flow rate. The flow meter sensor includes a pipe and a flow detection device connected to the pipe for detecting the flow rate of fluid within the pipe. The pipe includes a first curved pipe section and a first straight pipe section connected to each other.

Description

Technical Field

[0001] This application relates to the field of sensor technology, and more particularly to a flow meter sensor. Background Technology

[0002] In long-distance natural gas pipelines and trade transactions, flow meter sensors are used to measure the operating volumetric flow rate of natural gas within the pipeline, facilitating the metering of natural gas trade.

[0003] In the prior art, the operating volumetric flow rate of natural gas (volumetric flow rate under actual temperature and pressure) measured by the flow meter sensor is compensated for temperature and pressure to convert the operating volumetric flow rate of natural gas into the standard volumetric flow rate under standard conditions.

[0004] However, the flow meter sensor mentioned above only performs temperature and pressure compensation when measuring the standard volumetric flow rate of natural gas, which may result in low accuracy of the flow meter sensor when measuring the natural gas flow rate, affecting the accuracy of the flow meter sensor in detecting the natural gas flow rate. Summary of the Invention

[0005] The purpose of this application is to provide a flow meter sensor that aims to solve the problem of how to improve the accuracy of flow meter sensors in detecting fluid flow.

[0006] To achieve the above objectives, this application adopts the following technical solution: This application provides a flow meter sensor, which includes a pipe and a flow detection device. The flow detection device is connected to the pipe and is used to detect the flow rate of fluid in the pipe. The pipe includes a first curved pipe section and a first straight pipe section connected to each other.

[0007] The flow meter sensor provided in this application embodiment, when installed in a fluid transportation pipeline, such as a natural gas transportation pipeline, arranges a first curved pipe section and a first straight pipe section sequentially along the fluid flow direction. During fluid transportation, the fluid first enters the first curved pipe section and then the first straight pipe section. Because the flow meter sensor pipeline is under high pressure for extended periods, the first curved pipe section undergoes elastic deformation to absorb the mechanical stress and slight expansion deformation generated by the pipe wall. In other words, the mechanical stress and slight expansion deformation generated by the pipe wall are primarily absorbed by the first curved pipe section, resulting in only minor deformation in the first straight pipe section. This reduces the deformation of the pipe wall in the first straight pipe section, improving the installation stability of the flow detection device arranged on the first straight pipe section, effectively suppressing zero-point drift of the instrument on the first straight pipe section, thereby improving the accuracy of the flow meter sensor detecting fluid flow on the first straight pipe section and ensuring the accuracy of high-pressure natural gas trade metering.

[0008] Furthermore, when a large flow rate (i.e., a high velocity) of fluid is introduced into the pipeline, the first curved pipe section can undergo significant elastic deformation due to its curved structure, absorbing the inertial impact energy generated when the fluid enters. In other words, the inertial impact energy generated by the fluid is primarily absorbed by the first curved pipe section, thereby reducing the inertial impact energy transmitted to the first straight pipe section. Simultaneously, compared to the straight pipe section, the curved structure of the first curved pipe section has better impact resistance, undergoing sufficient elastic deformation upon impact and being less prone to permanent deformation that would cause it to lose its elastic function. This protects the flow detection device inside the pipeline from the impact of large flow rates, thereby improving the service life and safety of the flow detection device under high pressure and high flow conditions.

[0009] In some embodiments, the inner diameter of the first curved pipe section is larger than the inner diameter of the first straight pipe section.

[0010] In some embodiments, the first curved pipe section is a corrugated pipe section that is wavy along the length of the pipe.

[0011] In some embodiments, the difference between the inner diameter of the corrugated pipe section and the inner diameter of the first straight pipe section is a first difference value, and the ratio of the first difference value to the inner diameter of the corrugated pipe section is greater than or equal to 0.3 and less than or equal to 0.5.

[0012] In some embodiments, the ratio of the height difference between the crest and trough of the wave section's axis to the inner diameter of the wave section is greater than or equal to 0.1 and less than or equal to 0.2.

[0013] In some embodiments, the pipeline further includes a connecting pipe section, which includes a second straight pipe section, a second curved pipe section, and a connecting plate. The second straight pipe section is connected to the first straight pipe section, and the inner diameter of the second straight pipe section is the same as that of the first straight pipe section.

[0014] A second curved pipe section is connected to the first curved pipe section and is tangent to the end of the first curved pipe section near the second straight pipe section. The second curved pipe section includes a first wall plate and a second wall plate arranged along a first direction. The inner diameter of the second curved pipe section is the same as the inner diameter of the first curved pipe section. The first direction is consistent with the arrangement direction of the recesses and protrusions of the first curved pipe section. The first wall plate is connected to the second straight pipe section, and the second wall plate is spaced apart from the second straight pipe section. A connecting plate is connected between the second wall plate and the second straight pipe section.

[0015] In some embodiments, the flow detection device includes a stress sensor, a flow velocity sensor, and a controller. The stress sensor is connected to a first curved pipe section and is used to detect the deformation stress of the first curved pipe section. The flow velocity sensor is disposed in the first curved pipe section and / or a first straight pipe section and is used to detect the operating flow velocity of the fluid in the pipe. Both the stress sensor and the flow velocity sensor are electrically connected to the controller, which is configured to: correct the cross-sectional area of ​​the pipe according to the deformation stress to obtain the actual cross-sectional area of ​​the pipe under fluid flow conditions; and calculate the operating volumetric flow rate of the fluid in the pipe based on the actual cross-sectional area and the operating flow velocity.

[0016] In some embodiments, the controller is further configured to calculate the actual cross-sectional area of ​​the first curved pipe segment according to the following formula: = ; in, This represents the actual cross-sectional area of ​​the first bend in the pipe section under fluid flow conditions. The cross-sectional area of ​​a pipe when no fluid is flowing through it; This is the stress influence coefficient; This represents the deformation stress of the first curved pipe section.

[0017] In some embodiments, the controller is further configured to: calculate the change in the cross-sectional area of ​​the pipe based on the deformation stress using an elastic modulus model, wherein the change in the cross-sectional area of ​​the pipe refers to the absolute value of the difference between the cross-sectional area of ​​the pipe before fluid is introduced and the cross-sectional area of ​​the pipe after fluid is introduced, and correct the actual cross-sectional area based on the change in the cross-sectional area.

[0018] In some embodiments, the flow rate sensor includes a first vortex sensor, a second vortex sensor, a first ultrasonic probe, and a second ultrasonic probe. The first vortex sensor is connected to a first curved pipe section, the second vortex sensor is connected to a first straight pipe section, the first ultrasonic probe is located in the first curved pipe section, and the second ultrasonic probe is located in the first straight pipe section.

[0019] The controller is also configured to calculate the first flow velocity of the fluid in the pipe based on the vortex frequency of the first vortex sensor and the vortex frequency of the second vortex sensor. The second flow velocity of the fluid in the pipe is calculated based on the time difference between the forward and reverse flow of the ultrasonic waves from the first ultrasonic probe and the ultrasonic waves from the second ultrasonic probe. The first and second flow velocities are calculated using the weighted average method to obtain the operating flow velocity of the fluid in the pipe.

[0020] In some embodiments, the flow meter sensor further includes a temperature and pressure sensor and a connecting pipe section, the connecting pipe section being connected between a first curved pipe section and a first straight pipe section, and the temperature and pressure sensor being disposed in the connecting pipe section for detecting the temperature and pressure of the fluid in the pipe.

[0021] The controller is electrically connected to the temperature and pressure sensor, and is also configured to convert the operating volumetric flow rate into the standard volumetric flow rate based on the temperature and pressure of the fluid in the pipeline using the gas equation. Attached Figure Description

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

[0023] Figure 1 A schematic diagram of the structure of a flow meter sensor provided in some embodiments of this application; Figure 2 for Figure 1 The diagram shows the structure of the pipe in the flow meter sensor. Figure 3 for Figure 1 The diagram shows the circuit connection of the flow detection device in the flow meter sensor. Figure 4 This application provides a flowchart of a method for measuring fluid flow rate in a pipe using a flow meter sensor, which is part of some embodiments of the present application.

[0024] Explanation of reference numerals in the attached figures: 10. Flow meter sensor; 1. Pipeline; 11. First curved pipe section; 111. Corrugated pipe section; 12. First straight pipe section; 13. Connecting pipe section; 131. Second straight pipe section; 132. Second curved pipe section; 1321. First wall plate; 1322. Second wall plate; 133. Connecting plate; 2. Flow detection device; 21. Stress sensor; 22. Flow velocity sensor; 221. First vortex sensor; 2211. First vortex generator; 222. Second vortex sensor; 2221. Second vortex generator; 223. First ultrasonic probe; 224. Second ultrasonic probe; 23. Temperature and pressure sensor; 231. Temperature sensor; 232. Pressure sensor. Detailed Implementation

[0025] The technical solutions of the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this application, and not all embodiments. Based on the embodiments of this application, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this application.

[0026] In the description of this application, it should be understood that the terms "upper," "lower," "left," "right," "front," "rear," "inner," and "outer," etc., indicate the orientation or positional relationship based on the orientation or relative positional relationship shown in the accompanying drawings. They are used only for the convenience of describing this application and for simplification, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this application. Unless otherwise specified, the above-mentioned orientational descriptions can be flexibly set in practical applications, provided that the relative positional relationships shown in the accompanying drawings are satisfied.

[0027] The terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Therefore, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of this application, unless otherwise stated, "a plurality of" means two or more.

[0028] In the description of this application, it should be noted that, unless otherwise expressly specified and limited, the terms "installation," "connection," "linking," and "communication" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection. They can refer to a direct connection or an indirect connection through an intermediate medium, or a connection within two components. Those skilled in the art can understand the specific meaning of the above terms in this application according to the specific circumstances.

[0029] In embodiments of this application, the terms "comprising," "including," or any other variations thereof are intended to cover non-exclusive inclusion, such that a process, article, or apparatus that comprises a list of elements includes not only those elements but also other elements not expressly listed, or elements inherent to such a process, article, or apparatus. Without further limitation, an element defined by the phrase "comprising one..." does not exclude the presence of other identical elements in the process, article, or apparatus that includes that element.

[0030] In the embodiments of this application, the terms "exemplary" or "for example" are used to indicate that something is an example, illustration, or description. Any embodiment or design that is described as "exemplary" or "for example" in the embodiments of this application should not be construed as being more preferred or advantageous than other embodiments or design. Specifically, the use of the terms "exemplary" or "for example" is intended to present the relevant concepts in a specific manner.

[0031] In the description of this specification, specific features, structures, materials, or characteristics may be combined in any suitable manner in one or more embodiments or examples.

[0032] In long-distance natural gas pipelines and trade transactions, since natural gas is a compressible fluid, its volume changes significantly with temperature and pressure. Therefore, the operating volumetric flow rate (or operating mass flow rate) of natural gas measured by the flow meter sensor 10 needs to be compensated for temperature and pressure to convert it into the volumetric flow rate (or mass flow rate) under standard conditions. Among them, the operating volumetric flow rate refers to the volumetric flow rate under actual temperature and pressure.

[0033] Trade transfer refers to the process by which natural gas is transferred from the seller to the buyer, and both parties measure, settle, and deliver the gas based on the volumetric flow rate under standard conditions after temperature and pressure compensation.

[0034] However, during natural gas transportation, the measuring tube of the flow meter sensor 10 is under high pressure for extended periods, which may cause significant circumferential mechanical stress and slight expansion deformation in the tube wall. Simultaneously, thermal stress from changes in ambient temperature also acts superimposed on the tube wall. This change in tube wall stiffness and deformation is directly transmitted to sensors mounted on the tube wall (such as piezoelectric sensing elements of vortex flow meters, the base of ultrasonic probes, etc.), causing the instrument to produce a non-zero output at zero flow, i.e., zero-point drift. Although the relative error of this zero-point drift under high-pressure, high-flow conditions is small, multiplied by the huge volume of natural gas trade, it will seriously affect the accuracy of high-pressure natural gas trade measurement, and may even lead to trade disputes. Trade disputes refer to contractual or legal disputes arising from differences in measurement data or inability to reach an agreement on settlement criteria (such as volumetric flow rate under standard conditions) between buyers and sellers.

[0035] Therefore, temperature and pressure compensation alone is not enough; stress compensation is also required to eliminate the structural mechanical effects of pipe wall deformation and sensor zero-point drift caused by high pressure and temperature changes. Combined with temperature and pressure compensation, the operating volumetric flow rate of natural gas is converted into the standard volumetric flow rate under standard conditions to ensure the accuracy of trade measurement.

[0036] Based on this, please refer to Figure 1 , Figure 1This is a schematic diagram of the structure of a flow meter sensor 10 provided in some embodiments of this application. The flow meter sensor 10 may include a pipe 1 and a flow detection device 2. The flow detection device 2 is connected to the pipe 1 and is used to detect the flow rate of fluid within the pipe 1. The pipe 1 may include a first curved pipe section 11 and a first straight pipe section 12 connected to each other. For example, the fluid may be natural gas.

[0037] The flow meter sensor 10 is connected to a flowing delivery pipe to detect the flow rate of the fluid. In some examples, the fluid delivery pipe may include a first pipe section and a second pipe section. The flow meter sensor 10 is connected between the first pipe section and the second pipe section, allowing the fluid to flow from the first pipe section through the flow meter sensor 10 and then into the second pipe section. For example, the first curved pipe section 11 of the flow meter sensor 10 may be connected between the first pipe section and the first straight pipe section 12, and the first straight pipe section 12 may be connected between the first curved pipe section 11 and the second pipe section.

[0038] The flow meter sensor 10 provided in this embodiment, through the arrangement of a first curved pipe section 11 and a first straight pipe section 12, allows the fluid to first enter the first curved pipe section and then the first straight pipe section during natural gas transportation. Since the pipe 1 of the flow meter sensor 10 is under high pressure for a long period, the first curved pipe section 11 undergoes elastic deformation to absorb the mechanical stress and slight expansion deformation generated by the pipe wall of pipe 1. In other words, the mechanical stress and slight expansion deformation generated by the pipe wall of pipe 1 are mainly absorbed by the first curved pipe section 11, resulting in only a small deformation in the first straight pipe section 12. This reduces the deformation of the pipe wall of the first straight pipe section 12, improving the installation stability of the flow detection device 2 arranged on the first straight pipe section 12, effectively suppressing the zero-point drift phenomenon of the instrument on the first straight pipe section 12, thereby improving the accuracy of the flow meter sensor 10 in detecting fluid flow on the first straight pipe section 12 and ensuring the accuracy of high-pressure natural gas trade metering.

[0039] It should be noted that the high-pressure state of pipe 1 of flow meter sensor 10 includes the following two states. The first is the high-pressure dynamic pressure state, for example, during the process of fluid being introduced into pipe 1 through the first section of pipe and during the process of fluid being discharged from pipe 1 through the second section of pipe. At this time, the fluid is flowing, and pipe 1 is in a high-pressure state. The second is the high-pressure static pressure state, for example, after fluid is introduced into pipe 1 through the first section of pipe, the fluid has not yet flowed, but pipe 1 is still in a high-pressure state.

[0040] Furthermore, when a large flow rate (i.e., a high velocity) of fluid is introduced into pipe 1, the first curved pipe section 11 can undergo significant elastic deformation due to its curved structure, absorbing the inertial impact energy generated when the fluid enters. In other words, the inertial impact energy generated by the fluid is primarily absorbed by the first curved pipe section 11, thereby reducing the inertial impact energy transmitted to the first straight pipe section 12. Simultaneously, compared to the straight pipe section, the curved structure of the first curved pipe section 11 has better impact resistance, undergoing sufficient elastic deformation upon impact and being less prone to permanent deformation and loss of elasticity. This protects the flow detection device 2 inside pipe 1 from the impact of the large flow rate, thereby improving the service life and safety of the flow detection device 2 under high pressure and high flow conditions.

[0041] In some examples, the first curved pipe section 11 and the first straight pipe section 12 can be integrally manufactured using a hydroforming process or a precision pipe bending process, so that the inner walls of the first curved pipe section 11 and the first straight pipe section 12 are smooth and without weld seams, reducing pressure loss and noise during high-pressure natural gas flow.

[0042] In some examples, the number of first curved pipe segments 11 and first straight pipe segments 12 can both be one. One first curved pipe segment 11 and one first straight pipe segment 12 are arranged axially along the pipe 1. Alternatively, the number of first curved pipe segments 11 and first straight pipe segments 12 can both be multiple, in which case the multiple first curved pipe segments 11 and multiple first straight pipe segments 12 are arranged alternately along the circumference of the pipe 1. For example, the number of multiple first curved pipe segments 11 and multiple first straight pipe segments 12 can be 2, 3, 4, 5, etc.

[0043] In some other examples, pipe 1 may consist only of the first bend segment 11. Alternatively, pipe 1 may consist only of the first straight segment 12.

[0044] In some embodiments, please refer to Figure 1 and Figure 2 , Figure 2 for Figure 1 The schematic diagram of the pipe 1 in the flow meter sensor 10 shown indicates that the inner diameter D1 of the first curved pipe section 11 is greater than the inner diameter D2 of the first straight pipe section 12. It should be noted that the inner diameter mentioned above in this application refers to the diameter.

[0045] In this way, by making the inner diameter of the first curved pipe section 11 larger than the inner diameter of the first straight pipe section 12, the larger inner diameter of the first curved pipe section 11 can reduce the resistance to fluid flow within the first curved pipe section 11, so as to ensure that the fluid in the first curved pipe section 11 flows smoothly into the first straight pipe section 12, reduce the pressure loss in fluid flow, thereby improving the accuracy of the flow meter sensor 10 in detecting fluid flow and ensuring the accuracy of high-pressure natural gas trade metering.

[0046] In some other embodiments, the inner diameter of the first curved pipe section 11 may be equal to or less than the inner diameter of the first straight pipe section 12, as long as the fluid in the first curved pipe section 11 can flow smoothly into the first straight pipe section 12.

[0047] In some embodiments, the first curved pipe section 11 is a wavy pipe section 111 that is wavy along the length of the pipe 1.

[0048] In this way, the corrugated pipe section 111 can undergo more significant bending deformation when mechanical stress and slight expansion deformation occur on the pipe wall of the first curved pipe section 11, thereby further improving the absorption effect of mechanical stress and slight expansion deformation. Furthermore, the corrugated pipe section 111 can better disperse the mechanical stress and slight expansion deformation it bears, further reducing the mechanical stress and slight expansion deformation transmitted to the first straight pipe section 12. This better ensures the installation stability of the flow detection device 2 on the first straight pipe section 12, effectively suppresses the zero-point drift phenomenon of the instrument on the first straight pipe section 12, and thus improves the accuracy of the flow meter sensor 10 on the first straight pipe section 12 when detecting fluid flow, ensuring the accuracy of high-pressure natural gas trade metering.

[0049] In addition, the wavy corrugated pipe section 111 has a simple structure and is easy to manufacture.

[0050] In some other embodiments, the first curved pipe segment 11 may also be a pipe segment with a curved structure such as an arc-shaped pipe segment or a spiral pipe segment.

[0051] In some embodiments, the inner diameter of the corrugated pipe section 111 is larger than the inner diameter of the first straight pipe section 12. The difference between the inner diameter of the corrugated pipe section 111 and the inner diameter of the first straight pipe section 12 is a first difference value. The ratio of the first difference value to the inner diameter of the corrugated pipe section 111 is greater than or equal to 0.3 and less than or equal to 0.5. For example, the ratio of the first difference value to the inner diameter of the corrugated pipe section 111 can be 0.3, 0.35, 0.4, 0.45, 0.5, etc.

[0052] The inner diameter of the corrugated pipe section 111 is the diameter of the corrugated pipe section 111, and the inner diameter of the first straight pipe section 12 is the diameter of the first straight pipe section 12.

[0053] In this way, if the ratio of the first difference to the inner diameter of the corrugated pipe section 111 is less than 0.3, the first difference is small. That is to say, the inner diameter of the corrugated pipe section 111 is not much different from the inner diameter of the first straight pipe section 12. The corrugated pipe section 111 with similar inner diameter has a limited ability to absorb mechanical stress and slight expansion deformation of the pipe wall under high pressure.

[0054] If the ratio of the first difference to the inner diameter of the corrugated pipe section 111 is greater than 0.5, the first difference is relatively large, which means that the inner diameter of the corrugated pipe section 111 is significantly larger than that of the first straight pipe section 12. Although the corrugated pipe section 111 with a larger inner diameter can reduce the resistance of fluid flow in the corrugated pipe section 111, when the fluid flows from the corrugated pipe section 111 with a larger inner diameter into the first straight pipe section 12 with a smaller inner diameter, it is easy to induce local turbulence and affect the flow stability of the fluid in the first straight pipe section 12.

[0055] Thus, when the ratio of the first difference to the inner diameter of the corrugated pipe section 111 is greater than or equal to 0.3 and less than or equal to 0.5, the deformation absorption capacity of the corrugated pipe section 111, as well as the flow resistance and flow stability of the fluid, can be taken into account.

[0056] In some embodiments, the ratio of the height difference H1 between the crests and troughs of the wave axis of the corrugated pipe section 111 to the inner diameter D1 of the corrugated pipe section 111 is greater than or equal to 0.1 and less than or equal to 0.2. For example, the ratio of the height difference H1 between the crests and troughs of the wave axis of the corrugated pipe section 111 to the inner diameter of the corrugated pipe section 111 can be 0.1, 0.12, 0.14, 0.16, 0.18, 0.2, etc.

[0057] In this way, if the ratio of the height difference between the crest and trough of the wave axis of the wave section 111 to the inner diameter of the wave section 111 is less than 0.1, the height difference between the crest and trough of the wave axis of the wave section 111 to the inner diameter of the wave section 111 is relatively small. In other words, when the inner diameter of the wave section 111 is constant, the height difference between the crest and trough of the wave axis of the wave section 111 is small, that is, the degree of undulation is small. The wave crest and trough of the wave axis of the wave section with a small height difference have a relatively limited ability to absorb mechanical stress and slight expansion deformation of the pipe wall under high pressure.

[0058] If the ratio of the height difference between the crest and trough of the wave axis of the wave section 111 to the inner diameter of the wave section 111 is greater than 0.2, then the ratio of the height difference between the crest and trough of the wave axis of the wave section 111 to the inner diameter of the wave section 111 is relatively large. In other words, with a fixed inner diameter of the wave section 111, the height difference between the crest and trough of the wave axis of the wave section 111 is relatively large, i.e., the degree of undulation is relatively large. Although a wave section 111 with a large height difference can enhance the elastic deformation capacity of the wave section 111, a wave section 111 with a large height difference may lead to an increase in the resistance of fluid flow within the wave section 111, affecting the smoothness of fluid flow.

[0059] Thus, when the ratio of the height difference between the crest and trough of the wave on the axis of the wave tube section 111 to the inner diameter of the wave tube section 111 is greater than or equal to 0.1 and less than or equal to 0.2, the deformation absorption capacity of the wave tube section 111 and the flow resistance of the fluid can be balanced.

[0060] This application exemplifies a situation where the ratio of the first difference to the inner diameter of the corrugated pipe section 111 is greater than or equal to 0.3 and less than or equal to 0.5, while the ratio of the height difference between the crests and troughs of the axis of the corrugated pipe section 111 to its inner diameter is greater than or equal to 0.1 and less than or equal to 0.2. This allows the corrugated pipe section 111 to have an S-shaped structure, ensuring both smooth fluid flow within the corrugated pipe section 111 and its ability to absorb mechanical stress and minor expansion deformation under high pressure.

[0061] In some embodiments, the pipe 1 may further include a connecting pipe section 13, which may include a second straight pipe section 131, a second curved pipe section 132 and a connecting plate 133. The second straight pipe section 131 is connected to the first straight pipe section 12, and the inner diameter of the second straight pipe section 131 is the same as the inner diameter of the first straight pipe section 12.

[0062] The second curved pipe section 132 is connected to the first curved pipe section 11 and is tangent to the end of the first curved pipe section 11 near the second straight pipe section 131. The second curved pipe section 132 may include a first wall plate 1321 and a second wall plate 1322 arranged along a first direction. The inner diameter of the second curved pipe section 132 is the same as the inner diameter of the first curved pipe section 11. The first direction is consistent with the arrangement direction of the recesses and protrusions of the first curved pipe section 11. The first wall plate 1321 is connected to the second straight pipe section 131, and the second wall plate 1322 is spaced apart from the second straight pipe section 131. A connecting plate 133 is connected between the second wall plate 1322 and the second straight pipe section 131.

[0063] In this way, the connection between the first straight pipe section 12 and the first curved pipe section 11 can be easily facilitated by the connection pipe section 13. Specifically, the second straight pipe section 131 is connected to the first straight pipe section 12. The inner diameter of the second straight pipe section 131 is the same as the inner diameter of the first straight pipe section 12. The fact that the first straight pipe section 12 and the second straight pipe section 131 have the same inner diameter allows the connection between the first straight pipe section 12 and the second straight pipe section 131 to fit tightly, thereby ensuring the sealing reliability of the connection between the first straight pipe section 12 and the second straight pipe section 131 and preventing fluid leakage at the connection between the first straight pipe section 12 and the second straight pipe section 131, which would affect the accuracy of the flow meter sensor 10 in detecting the fluid flow rate.

[0064] In addition, the first straight pipe section 12 and the second straight pipe section 131 with the same inner diameter can simplify the connection process between the first straight pipe section 12 and the second straight pipe section 131 and reduce the installation difficulty.

[0065] The second curved pipe section 132 is connected to the first curved pipe section 11 and is tangent to the end of the first curved pipe section 11 near the second straight pipe section 131. The inner diameter of the second curved pipe section 132 is the same as the inner diameter of the first curved pipe section 11. The fact that the first curved pipe section 11 and the second curved pipe section 132 have the same inner diameter allows the connection between the first curved pipe section 11 and the second curved pipe section 132 to fit tightly, thereby ensuring the sealing reliability of the connection between the first curved pipe section 11 and the second curved pipe section 132 and preventing fluid leakage at the connection between the first curved pipe section 11 and the second curved pipe section 132, which would affect the accuracy of the flow meter sensor 10 in detecting the fluid flow rate.

[0066] Meanwhile, the fact that the first curved pipe section 11 and the second curved pipe section 132 have the same inner diameter can simplify the connection process between the first curved pipe section 11 and the second curved pipe section 132 and reduce the installation difficulty.

[0067] Furthermore, by connecting the second curved pipe section 132 to the first curved pipe section 11 and making it tangent to the end of the first curved pipe section 11 near the second straight pipe section 131, a smooth transition of the flow path at the connection between the first curved pipe section 11 and the second curved pipe section 132 can be ensured, so as to avoid the generation of steps or sharp corners. This can reduce the flow resistance of the fluid from the first curved pipe section 11 to the second curved pipe section 132 and ensure the smooth flow of the fluid from the first curved pipe section 11 to the second curved pipe section 132.

[0068] The second curved pipe section 132 may include a first wall plate 1321 and a second wall plate 1322 arranged along a first direction. The first wall plate 1321 is connected to the second straight pipe section 131, and the second wall plate 1322 is spaced apart from the second straight pipe section 131. This allows the flow direction of the fluid in the first curved pipe section 11 to be consistent with the flow direction of the fluid in the second curved pipe section 132, thereby improving the uniformity of stress when the first curved pipe section 11 and the second curved pipe section 132 are deformed.

[0069] Based on this, by connecting the connecting plate 133 between the second wall plate 1322 and the second straight pipe section 131, a conical transition zone can be formed between the first wall plate 1321, the second wall plate 1322 and the connecting plate 133. This conical transition zone can effectively smooth the difference in inner diameter between the first curved pipe section 11 and the first straight pipe section 12, so as to avoid stress concentration at the connection between the first curved pipe section 11 and the first straight pipe section 12. Thus, while ensuring the smooth flow of high-pressure natural gas, the structural reliability of the connection between the first curved pipe section 11 and the first straight pipe section 12 can be enhanced.

[0070] In some examples, the wall thickness of the connecting pipe segment 13 is greater than the wall thickness of the first bent pipe segment 11 and greater than the wall thickness of the first straight pipe segment 12. This can improve the connection strength between the connecting pipe segment 13 and the first bent pipe segment 11, as well as the connection strength between the connecting pipe segment 13 and the first straight pipe segment 12.

[0071] In some examples, the end face of the first bent pipe section 11 facing the second bent pipe section 132 is a bevel, and the end face of the second bent pipe section 132 facing the first bent pipe section 11 is a reverse bevel that fits closely to it. This increases the contact area at the connection between the first bent pipe section 11 and the second bent pipe section 132, creating a self-sealing effect during high-pressure tightening, ensuring that the interface dimensions at the connection between the first bent pipe section 11 and the second bent pipe section 132 are consistent and resistant to high-pressure impact.

[0072] In some embodiments, please refer to Figures 1 to 3 , Figure 3 for Figure 1 The diagram shows the circuit connection of the flow detection device 2 in the flow meter sensor 10. The flow detection device 2 may include a stress sensor 21, a flow velocity sensor 22, and a controller. The stress sensor 21 is connected to the first curved pipe section 11 and is used to detect the deformation stress of the first curved pipe section 11. The flow velocity sensor 22 is located in the first curved pipe section 11 and / or the first straight pipe section 12 and is used to detect the operating flow velocity of the fluid in the pipe 1.

[0073] Both stress sensor 21 and flow velocity sensor 22 are electrically connected to the controller, which is configured to correct the cross-sectional area of ​​pipe 1 based on deformation stress to obtain the actual cross-sectional area of ​​pipe 1 under fluid flow conditions. The controller then calculates the operating volumetric flow rate of the fluid within pipe 1 based on the actual cross-sectional area and the operating flow velocity.

[0074] The cross-sectional area refers to the area of ​​the cross section perpendicular to the pipe's axial direction.

[0075] In this way, during the fluid transport process, the pipe 1 of the flow meter sensor 10 is under high pressure for a long time. Since the mechanical stress and slight expansion deformation generated by the pipe wall of the pipe 1 are mainly absorbed by the first curved pipe section 11, while the deformation of the pipe wall of the first straight pipe section 12 is small and can be ignored. Therefore, only the mechanical stress and slight expansion deformation generated by the pipe wall of the first curved pipe section 11 need to be corrected.

[0076] By connecting the stress sensor 21 to the first curved pipe section 11, the stress sensor 21 can detect the deformation stress that occurs in the first curved pipe section 11 when fluid flows. This deformation stress is used to correct the effects of the circumferential mechanical stress generated on the pipe wall of the first curved pipe section 11 and the slight expansion deformation.

[0077] Meanwhile, by placing the flow velocity sensor 22 in the first curved pipe section 11 and / or the first straight pipe section 12, the flow velocity sensor 22 can detect the flow velocity of the fluid in the first curved pipe section 11 and / or the first straight pipe section 12 when the fluid is flowing, so as to facilitate the subsequent calculation of the working condition volumetric flow rate or working condition mass flow rate of the fluid in the pipe 1.

[0078] Based on this, by electrically connecting both the stress sensor 21 and the flow velocity sensor 22 to the controller, the controller can correct the cross-sectional area of ​​the pipe 1 according to the deformation stress to obtain the actual cross-sectional area of ​​the pipe 1 under fluid flow conditions. The volumetric flow rate of the fluid in the pipe 1 is calculated based on the actual cross-sectional area and flow velocity, thereby improving the detection accuracy of the flow meter sensor 10 under high pressure conditions, effectively suppressing zero-point drift, and ensuring the accuracy of high-pressure natural gas trade metering.

[0079] It should be noted that the actual cross-sectional area of ​​pipe 1 under fluid flow conditions is calculated by weighted average of the actual cross-sectional area of ​​the first curved pipe section 11 after deformation stress correction and the cross-sectional area of ​​the first straight pipe section 12.

[0080] In some examples, the flow rate sensor 22 is located in the first curved pipe section 11. Alternatively, the flow rate sensor 22 is located in the first straight pipe section 12. Alternatively, the flow rate sensor 22 is located in both the first curved pipe section 11 and the first straight pipe section 12.

[0081] This application is illustrated by way of example with flow rate sensor 22 installed in the first curved pipe section 11 and the first straight pipe section 12.

[0082] In some embodiments, the controller is further configured to calculate the actual cross-sectional area of ​​the first curved pipe segment according to the following formula: = ; in, This is the actual cross-sectional area of ​​the first bend in the pipe section under fluid flow conditions. The cross-sectional area of ​​a pipe when no fluid is flowing through it; This is the stress influence coefficient; This represents the deformation stress of the first curved pipe section.

[0083] In this way, the controller can correct the cross-sectional area of ​​the first curved pipe section 11 based on the deformation stress detected by the stress sensor 21. Then, by combining the corrected actual cross-sectional area of ​​the first curved pipe section 11 with the cross-sectional area of ​​the first straight pipe section 12, a weighted average algorithm is used to calculate the actual cross-sectional area of ​​the pipe 1, and then the working volume flow rate of the fluid in the pipe can be calculated. This can improve the detection accuracy of the flow meter sensor 10 under high pressure, effectively suppress zero drift, and ensure the accuracy of high-pressure natural gas trade measurement.

[0084] In some embodiments, the controller is further configured to: calculate the change in the cross-sectional area of ​​pipe 1 based on the deformation stress using an elastic modulus model, wherein the change in the cross-sectional area of ​​pipe 1 refers to the absolute value of the difference between the cross-sectional area of ​​pipe 1 before fluid is introduced and the cross-sectional area of ​​pipe 1 after fluid is introduced, and correct the actual cross-sectional area based on the change in the cross-sectional area.

[0085] In this way, the controller can calculate the change in the cross-sectional area of ​​pipe 1 using the elastic modulus model based on the deformation stress of the bent pipe section detected by the stress sensor 21, and then correct the actual cross-sectional area calculated above based on the change in cross-sectional area. Specifically, if the cross-sectional area of ​​pipe 1 increases after fluid is introduced, then the cross-sectional area of ​​pipe 1 after fluid is introduced is equal to the cross-sectional area of ​​pipe 1 before fluid is introduced plus the change in the cross-sectional area of ​​pipe 1. By comparing the calculated cross-sectional area value of pipe 1 after fluid is introduced with the actual cross-sectional area, if the error between the cross-sectional area value of pipe 1 after fluid is introduced and the actual cross-sectional area is within an effective range, it indicates that the actual cross-sectional area under the stress correction is relatively accurate. This can improve the detection accuracy of the flow meter sensor 10 arranged on the first bent pipe section 11 under high pressure static pressure conditions, effectively suppress zero drift, and ensure the accuracy of high-pressure natural gas trade measurement.

[0086] In some embodiments, the flow rate sensor 22 may include a first vortex sensor 221, a second vortex sensor 222, a first ultrasonic probe 223, and a second ultrasonic probe 224. The first vortex sensor 221 is connected to the first curved pipe section 11, the second vortex sensor 222 is connected to the first straight pipe section 12, the first ultrasonic probe 223 is disposed in the first curved pipe section 11, and the second ultrasonic probe 224 is disposed in the first straight pipe section 12.

[0087] The controller is also configured to calculate the first flow velocity of the fluid in the pipe 1 based on the vortex frequency of the first vortex sensor 221 and the vortex frequency of the second vortex sensor 222. The second flow velocity of the fluid in pipe 1 is calculated based on the time difference between the forward and reverse flow of the ultrasonic waves from the first ultrasonic probe 223 and the second ultrasonic probe 224. The first and second flow velocities are calculated using the weighted average method to obtain the operating flow velocity of the fluid in pipe 1.

[0088] The first vortex street sensor 221 and the second vortex street sensor 222 are both based on the Karman vortex street principle. By setting a vortex generator in the fluid, when the fluid flows through the vortex generator in the pipe 1, regular vortices are alternately generated from both sides of the vortex generator. The flow velocity is calculated by detecting the vortex frequency.

[0089] Specifically, the first vortex sensor 221 may include a first vortex generator 2211, which contains a first piezoelectric crystal. When fluid flows through the first vortex generator 2211 within the first curved pipe section 11, periodic pressure pulsations are generated from both sides of the first vortex generator 2211. These pressure pulsations act on the first piezoelectric crystal, causing it to generate a charge signal with the same frequency as the vortex, thereby obtaining the vortex frequency of the first vortex sensor 221. For example, the cross-sectional shape of the first vortex generator 2211 may be semi-circular, rectangular, or similar.

[0090] The second vortex shedding sensor 222 may include a second vortex generator 2221, which contains a second piezoelectric crystal. When fluid flows through the second vortex generator 2221 within the first straight pipe section 12, periodic pressure pulsations are generated from both sides of the second vortex generator 2221. These pressure pulsations act on the second piezoelectric crystal, causing it to generate a charge signal with the same frequency as the vortex shedding, thereby allowing the vortex shedding frequency of the second vortex shedding sensor 222 to be obtained. For example, the cross-sectional shape of the first vortex generator 2211 and the cross-sectional shape of the second vortex generator 2221 may be the same.

[0091] In some examples, the cross-sectional shape of the first vortex generator 2211 can be rectangular, and the ratio of the length of the cross-sectional shape of the first vortex generator 2211 to the inner diameter of the wave tube section 111 is greater than or equal to 0.2 and less than or equal to 0.3. For example, the ratio of the length of the cross-sectional shape of the first vortex generator 2211 to the inner diameter of the wave tube section 111 can be 0.2, 0.22, 0.24, 0.26, 0.28, 0.3, etc.

[0092] In some examples, the cross-sectional shape of the first vortex generator 2211 can be rectangular, and the ratio of the width of the cross-sectional shape of the first vortex generator 2211 to the inner diameter of the wave tube section 111 is greater than or equal to 0.05 and less than or equal to 0.1. For example, the ratio of the width of the cross-sectional shape of the first vortex generator 2211 to the inner diameter of the wave tube section 111 can be 0.05, 0.06, 0.07, 0.08, 0.09, 0.1, etc.

[0093] If the ratio of the length of the cross-sectional shape of the first vortex generator 2211 to the inner diameter of the wave tube section 111 is greater than 0.3, and the ratio of the width of the cross-sectional shape of the first vortex generator 2211 to the inner diameter of the wave tube section 111 is greater than 0.1, the cross-sectional area of ​​the first vortex generator 2211 is too large, which may lead to an increase in pressure loss when the fluid flows through the first vortex generator 2211, and at the same time, the fluid impact force is too strong, which may easily damage the components.

[0094] If the ratio of the length of the cross-sectional shape of the first vortex generator 2211 to the inner diameter of the wave tube section 111 is less than 0.2, and the ratio of the width of the cross-sectional shape of the first vortex generator 2211 to the inner diameter of the wave tube section 111 is greater than 0.05, the cross-sectional area of ​​the first vortex generator 2211 is too small, which may result in a weak signal when the fluid flows through the first vortex generator 2211, making it impossible to measure at low flow rates, and it is also highly susceptible to interference from on-site vibrations.

[0095] Thus, when the ratio of the length of the cross-sectional shape of the first vortex generator 2211 to the inner diameter of the wave tube section 111 is greater than or equal to 0.2 and less than or equal to 0.3, and the ratio of the width of the cross-sectional shape of the first vortex generator 2211 to the inner diameter of the wave tube section 111 is greater than or equal to 0.05 and less than or equal to 0.1, both signal clarity and equipment safety can be taken into account.

[0096] In some examples, the cross-sectional shape of the second vortex generator 2221 may also be rectangular. The ratio of the length of the cross-sectional shape of the second vortex generator 2221 to the inner diameter of the first straight pipe section 12 is greater than or equal to 0.2 and less than or equal to 0.3. The ratio of the width of the cross-sectional shape of the second vortex generator 2221 to the inner diameter of the first straight pipe section 12 is greater than or equal to 0.05 and less than or equal to 0.1.

[0097] The principle of the ratio of the length of the cross-sectional shape of the second vortex generator 2221 to the inner diameter of the first straight pipe section 12 is the same as the principle of the ratio of the length of the cross-sectional shape of the first vortex generator 2211 to the inner diameter of the wave pipe section 111. Similarly, the principle of the ratio of the width of the cross-sectional shape of the second vortex generator 2221 to the inner diameter of the first straight pipe section 12 is the same as the principle of the ratio of the width of the cross-sectional shape of the first vortex generator 2211 to the inner diameter of the wave pipe section 111. These principles will not be repeated here.

[0098] Next, the controller calculates the vortex frequency detected by the first vortex sensor 221 and the vortex frequency detected by the second vortex sensor 222 according to the weighted average method to obtain the vortex frequency of the fluid in the pipe 1, and then calculates the first flow velocity of the fluid in the pipe 1 based on the vortex frequency.

[0099] Specifically, the initial velocity of the fluid inside the pipe can be obtained using the following formula:

[0100] in, The first velocity of the fluid inside the pipe, expressed in m / s; f is the vortex frequency of the fluid inside the pipe, in Hz; K is the vortex flow meter coefficient, which is usually determined based on actual flow calibration. Actual flow calibration refers to the process of installing the flow meter in a real fluid pipeline, connecting it in series with a high-precision standard measuring device (such as a standard meter, weighing tank, or volumetric tank), and comparing and determining the flow meter coefficient (such as the vortex flow meter coefficient K) by actually passing through the fluid.

[0101] Both the first ultrasonic probe 223 and the second ultrasonic probe 224 use the time difference method for measurement. By detecting the time difference between the downstream and upstream propagation of the ultrasonic beam in the fluid, and combining the sound path and sound velocity, the flow velocity is calculated.

[0102] Specifically, the first ultrasonic probe 223 is installed in the first curved pipe section 11 (i.e., upstream of pipe 1), and the second ultrasonic probe 224 is installed in the first straight pipe section 12 (i.e., downstream of pipe 1). When the upstream first ultrasonic probe 223 emits an ultrasonic signal and the downstream second ultrasonic probe 224 receives the ultrasonic signal, the ultrasonic wave propagates in the same direction as the fluid flow, which is called downstream flow, and the propagation time is relatively short. When the downstream second ultrasonic probe 224 emits an ultrasonic signal and the upstream first ultrasonic probe 223 receives the ultrasonic signal, the ultrasonic wave propagates in the opposite direction to the fluid flow, which is called upstream flow, and the propagation time is relatively long.

[0103] For example, both the first ultrasonic probe 223 and the second ultrasonic probe 224 can be made of high-frequency piezoelectric ceramic material and encapsulated in a high-pressure resistant and corrosion-resistant stainless steel shell to obtain good waterproof sealing performance.

[0104] Next, the controller calculates the second flow velocity of the fluid in pipe 1 based on the forward and reverse flow time difference measured by the first ultrasonic probe 223 and the second ultrasonic probe 224, combined with the channel length and channel angle.

[0105] Specifically, the second velocity of the fluid inside the pipe can be obtained using the following formula:

[0106] in, The second velocity of the fluid inside the pipe is expressed in m / s. L is the channel length, which is the straight-line distance between the first and second ultrasonic probes, in meters. The channel angle is the angle between the direction of ultrasonic wave propagation and the axis of the pipe, measured in degrees. The time for ultrasound to travel backwards in a fluid. The unit is seconds (s). This is the time it takes for an ultrasonic wave to propagate downstream in a fluid, measured in seconds (s).

[0107] Next, the controller can dynamically allocate vortex shedding weights and ultrasonic weights based on the first and second flow velocities. When the flow velocity is high (strong turbulence), the vortex shedding weight is increased; when the flow velocity is low (laminar or transitional flow), the ultrasonic weight is increased. Then, by using a weighted average method to calculate the first and second flow velocities, the operating velocity of the fluid in the pipe can be obtained.

[0108] Specifically, the operating velocity of the fluid inside the pipe can be obtained using the following formula: v = W1·v1 + W2·v2 Where v is the operating velocity of the fluid in the pipe, in m / s; W1 is the vortex shear weight, W2 is the ultrasonic weight, and W1+W2=1.

[0109] Thus, the weighted average method is simple to calculate, has strong real-time performance, and can effectively suppress the interference of common-mode noise such as pipe wall vibration on the single flow velocity signal, thereby improving the reliability and accuracy of flow velocity measurement.

[0110] In some examples, the flow meter sensor 10 may also include a charge amplifier, a multiplexer, and an A / D converter. The charge amplifier and multiplexer are electrically connected to the A / D converter, and the multiplexer is electrically connected to both the A / D converter and the controller. Both the first vortex sensor 221 and the second vortex sensor 222 are electrically connected to the charge amplifier. The charge amplifier converts the weak charge signal generated by the first piezoelectric crystal into a low-impedance voltage signal, and also converts the weak charge signal generated by the second piezoelectric crystal into a low-impedance voltage signal. The A / D converter is connected between the multiplexer and the controller to convert the voltage signals into digital signals. The controller filters the converted digital signals and calculates the first flow velocity.

[0111] In some examples, the flow meter sensor 10 may also include a drive and receive circuit, a multiplexer, and an A / D converter. The drive and receive circuit is electrically connected to the multiplexer and A / D converter; the multiplexer is electrically connected to the A / D converter and the controller; and both the first ultrasonic probe 223 and the second ultrasonic probe 224 are electrically connected to the drive and receive circuit. The drive and receive circuit is used to transmit high-voltage pulses to excite the first ultrasonic probe 223 to emit ultrasonic signals and to receive the echo signals from the second ultrasonic probe 224. It is also used to transmit high-voltage pulses to excite the second ultrasonic probe 224 to emit ultrasonic signals and to receive the echo signals from the first ultrasonic probe 223. The A / D converter is connected between the multiplexer and the controller and is used to convert the received echo signals into digital signals. The controller filters the converted digital signals and calculates the second flow velocity.

[0112] In some examples, the flow meter sensor 10 may also include a bridge circuit, a multiplexer, and an A / D converter. The bridge circuit, multiplexer, and A / D converter are electrically connected, the multiplexer is electrically connected to the A / D converter and the controller, and the bridge circuit is also electrically connected to the stress sensor 21 to convert the resistance or strain change detected by the stress sensor 21 into a voltage signal. The A / D converter is connected between the multiplexer and the controller to convert the voltage signal into a digital signal. The controller filters the converted digital signal and calculates the deformation stress of the bent pipe section.

[0113] In some embodiments, the flow meter sensor 10 may further include a temperature and pressure sensor 23 and a connecting pipe section 13, the connecting pipe section 13 being connected between a first curved pipe section 11 and a first straight pipe section 12, and the temperature and pressure sensor 23 being disposed in the connecting pipe section 13 for detecting the temperature and pressure of the fluid in the pipe 1.

[0114] The controller is electrically connected to the temperature and pressure sensor 23. The controller is also configured to convert the operating volume flow rate into the standard volume flow rate based on the temperature and pressure of the fluid in the pipe 1 using the gas equation.

[0115] In this way, based on the stress correction mentioned above, the effects of circumferential mechanical stress and slight expansion deformation generated by the pipe wall of the first curved pipe section 11 under high pressure can be eliminated. The controller converts the working condition volumetric flow rate into the standard condition volumetric flow rate through the gas equation based on the temperature and pressure of the fluid in the pipe 1 detected by the temperature and pressure sensor 23. This can improve the detection accuracy of the flow meter sensor 10 under high pressure, effectively suppress zero drift, and ensure the accuracy of high-pressure natural gas trade measurement.

[0116] In some examples, the temperature and pressure sensor 23 includes a temperature sensor 231 and a pressure sensor 232, wherein the temperature sensor 231 is used to detect the temperature of the fluid in the pipe 1 and the pressure sensor 232 is used to detect the pressure of the fluid in the pipe 1.

[0117] In some examples, the temperature sensor 231 and the pressure sensor 232 can be an integrated structure to reduce the space occupied by the temperature and pressure sensors 23 in the flow meter sensor 10, thereby making the structure of the flow meter sensor 10 more compact. Alternatively, the temperature sensor 231 and the pressure sensor 232 can also be separate structures.

[0118] In some examples, the flow meter sensor 10 may also include a signal conditioning circuit, a multiplexer, and an A / D converter. The signal conditioning circuit is electrically connected to the multiplexer and the A / D converter, which in turn is electrically connected to the controller. The signal conditioning circuit is also electrically connected to the temperature and pressure sensor 23, and is used to convert the weak, noisy raw physical signal acquired by the temperature and pressure sensor 23 into a standardized voltage signal that the controller can recognize and process. The A / D converter is connected between the multiplexer and the controller, and is used to convert the voltage signal into a digital signal. The controller filters the converted digital signal and calculates the temperature and pressure of the fluid in pipe 1.

[0119] In some examples, the flow meter sensor 10 may also include a memory, a display screen, and a buzzer. The memory, display module, and buzzer are all electrically connected to the controller. The memory is used to store parameters such as the vortex meter coefficient, stress correction factor, and pipe diameter 1. The display screen is used to display information such as the operating flow velocity, the actual cross-sectional area of ​​pipe 1, the standard volumetric flow rate, fluid temperature, and fluid pressure in real time.

[0120] The buzzer is used to issue an alarm signal when the controller outputs a high level, indicating an overload. For example, when the controller calculates that the operating velocity of the fluid in pipe 1 exceeds a preset safety threshold (such as 10 m / s or 15 m / s), the controller outputs a high level to trigger the buzzer alarm, indicating an overload or risk of air hammer.

[0121] Among them, air hammer refers to the violent pressure fluctuation and impact phenomenon generated when high-pressure gas is rapidly started and stopped or its flow rate changes suddenly in pipeline 1, due to fluid inertia and compressibility, similar to the "water hammer" effect of liquid.

[0122] For details, please refer to Figures 1 to 4 , Figure 4 The flowchart illustrates a method for measuring fluid flow rate in a pipeline using a flow meter sensor, as provided in some embodiments of this application. For example, when measuring the fluid flow rate in pipeline 1, if the fluid is natural gas, the steps for calculating the standard volumetric flow rate of natural gas are as follows: S1: Flow sensor initialization and self-test.

[0123] Specifically, the flow sensor is powered on, so that the controller, stress sensor 21, first vortex sensor 221, second vortex sensor 222, first ultrasonic probe 223, second ultrasonic probe 224, and temperature and pressure sensor 23 are all in the powered-on state. The controller reads parameters such as vortex meter coefficient, stress correction factor, and pipe diameter from the memory.

[0124] S2: The controller synchronously acquires signals such as stress, vortex shedding, ultrasound, temperature, and pressure at the same time.

[0125] Specifically, a stress sensor 21 is connected to the first curved pipe section 11 to obtain the deformation stress of the first curved pipe section 11 detected by the stress sensor 21. A first vortex sensor 221 is connected to the first curved pipe section 11 to obtain the vortex frequency detected by the first vortex sensor 221. A second vortex sensor 222 is connected to the first straight pipe section 12 to obtain the vortex frequency detected by the second vortex sensor 222. A first ultrasonic probe 223 is installed in the first curved pipe section 11, and a second ultrasonic probe 224 is installed in the first straight pipe section 12 to obtain the forward and reverse flow time difference measured by the first ultrasonic probe 223 and the second ultrasonic probe 224. A temperature and pressure sensor 23 is installed in the connecting pipe section 13 to obtain the temperature and pressure of the fluid in the pipe 1.

[0126] S3: Calculate the first and second flow velocities of natural gas in pipeline 1.

[0127] Specifically, the controller calculates the first flow velocity of natural gas in pipeline 1 based on the vortex frequency of the first vortex sensor 221 and the vortex frequency of the second vortex sensor 222, and calculates the second flow velocity of natural gas in pipeline 1 based on the time difference between the forward and reverse flow of the ultrasonic waves emitted by the first ultrasonic probe 223 and the second ultrasonic probe 224.

[0128] S4: Correct the cross-sectional area of ​​pipe 1.

[0129] Specifically, the controller corrects the cross-sectional area of ​​pipe 1 based on deformation stress to obtain the actual cross-sectional area of ​​pipe 1 under natural gas flow conditions. It then calculates the change in the cross-sectional area of ​​pipe 1 using an elastic modulus model and corrects the actual cross-sectional area based on this change.

[0130] S5: Calculate the operating flow velocity of natural gas in pipeline 1.

[0131] Specifically, the controller calculates the first and second flow velocities using a weighted average method to obtain the operating flow velocity of the fluid in pipe 1.

[0132] S6: Calculate the standard volumetric flow rate of natural gas in pipeline 1.

[0133] Specifically, the controller calculates the operating volumetric flow rate of natural gas in pipeline 1 based on the actual cross-sectional area and operating flow velocity, and converts the operating volumetric flow rate into the standard volumetric flow rate through the gas equation.

[0134] S7: Security monitoring.

[0135] Specifically, when the controller calculates that the operating flow rate of the fluid in pipe 1 exceeds the preset safety threshold, the controller outputs a high level to trigger a buzzer alarm and records the over-limit time for subsequent life assessment. When the controller calculates that the operating flow rate of the fluid in pipe 1 does not exceed the preset safety threshold, it updates the display data and returns to step S2 for the next sampling cycle.

[0136] The above are merely specific embodiments of this application, but the scope of protection of this application is not limited thereto. Any variations or substitutions that can be easily conceived by those skilled in the art within the scope of the technology disclosed in this application should be included within the scope of protection of this application. Therefore, the scope of protection of this application should be determined by the scope of the claims.

Claims

1. A flow meter sensor, characterized in that, It includes a pipe (1) and a flow detection device (2), the flow detection device (2) being connected to the pipe (1) for detecting the flow rate of fluid in the pipe (1); the pipe (1) includes a first curved pipe section (11) and a first straight pipe section (12) connected to each other.

2. The flow meter sensor according to claim 1, characterized in that, The inner diameter of the first curved pipe section (11) is greater than the inner diameter of the first straight pipe section (12).

3. The flow meter sensor according to claim 1 or 2, characterized in that, The first curved pipe section (11) is a wavy pipe section (111) that is wavy along the length of the pipe (1).

4. The flow meter sensor according to claim 3, characterized in that, The difference between the inner diameter of the corrugated pipe section (111) and the inner diameter of the first straight pipe section (12) is the first difference value. The ratio of the first difference value to the inner diameter of the corrugated pipe section (111) is greater than or equal to 0.3 and less than or equal to 0.

5. And / or, the ratio of the height difference between the crest and trough of the axis of the wave section (111) to the inner diameter of the wave section (111) is greater than or equal to 0.1 and less than or equal to 0.

2.

5. The flow meter sensor according to claim 2, characterized in that, The pipeline (1) further includes a connecting pipe section (13), which includes: The second straight pipe section (131) is connected to the first straight pipe section (12), and the inner diameter of the second straight pipe section (131) is the same as the inner diameter of the first straight pipe section (12). The second curved pipe section (132) is connected to the first curved pipe section (11) and is tangent to the end of the first curved pipe section (11) near the straight section. The second curved pipe section (132) includes a first wall plate (1321) and a second wall plate arranged along a first direction. The inner diameter of the second curved pipe section (132) is the same as the inner diameter of the first curved pipe section (11). The first direction is consistent with the arrangement direction of the recess and protrusion of the first curved pipe section (11). The first wall plate (1321) is connected to the second straight pipe section (131), and the second wall plate (1322) is spaced apart from the second straight pipe section (131). A connecting plate (133) is connected between the second wall panel (1322) and the second straight pipe section (131).

6. The flow meter sensor according to claim 1, characterized in that, The flow detection device (2) includes: A stress sensor (21) is connected to the first bent pipe section (11) and is used to detect the deformation stress of the first bent pipe section (11). A flow rate sensor (22) is provided in the first curved pipe section (11) and / or the first straight pipe section (12) for detecting the working flow rate of the fluid in the pipe (1); The controller, the stress sensor (21) and the flow velocity sensor (22) are both electrically connected to the controller, the controller is configured to: correct the cross-sectional area of ​​the pipe (1) according to the deformation stress to obtain the actual cross-sectional area of ​​the pipe (1) under fluid flow conditions; The working volume flow rate of the fluid in the pipe (1) is calculated based on the actual cross-sectional area and the working condition flow velocity.

7. The flow meter sensor according to claim 6, characterized in that, The controller is also configured to calculate the actual cross-sectional area of ​​the first curved pipe segment (11) according to the following formula: = ； in, This represents the actual cross-sectional area of ​​the first curved pipe section 11 of pipe 1 when fluid is flowing; This is the stress influence coefficient; This represents the deformation stress of the first curved pipe section 11.

8. The flow meter sensor according to claim 6, characterized in that, The controller is also configured to: The change in the cross-sectional area of ​​the pipe (1) is calculated based on the deformation stress using the elastic modulus model. The change in the cross-sectional area of ​​the pipe (1) refers to the absolute value of the difference between the cross-sectional area of ​​the pipe (1) before fluid is introduced and the cross-sectional area of ​​the pipe (1) after fluid is introduced. The actual cross-sectional area is corrected based on the change in the cross-sectional area.

9. The flow meter sensor according to claim 6, characterized in that, The flow rate sensor (22) includes: A first vortex sensor (221) and a second vortex sensor (222), wherein the first vortex sensor (221) is connected to the first curved pipe section (11) and the second vortex sensor (222) is connected to the first straight pipe section (12); A first ultrasonic probe (223) and a second ultrasonic probe (224), wherein the first ultrasonic probe (223) is located in the first curved pipe section (11) and the second ultrasonic probe (224) is located in the first straight pipe section (12). The controller is also configured to calculate a first flow velocity of the fluid in the pipe (1) based on the vortex frequency of the first vortex sensor (221) and the vortex frequency of the second vortex sensor (222); The second flow velocity of the fluid in the pipe (1) is calculated based on the time difference between the forward and reverse flow of the ultrasonic waves from the first ultrasonic probe (223) and the second ultrasonic probe (224). The first flow velocity and the second flow velocity are calculated using the weighted average method to obtain the working flow velocity of the fluid in the pipe (1).

10. The flow meter sensor according to claim 9, characterized in that, It also includes a temperature and pressure sensor (23) and a connecting pipe section (13), the connecting pipe section (13) being connected between the first curved pipe section (11) and the first straight pipe section (12), the temperature and pressure sensor (23) being located in the connecting pipe section (13) for detecting the temperature and pressure of the fluid in the pipe (1); The controller is electrically connected to the temperature and pressure sensor (23), and the controller is also configured to convert the operating condition volumetric flow rate into the standard condition volumetric flow rate by means of the gas equation based on the temperature and pressure of the fluid in the pipe (1).

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