Sensor for pipeline fluid-solid coupling simulation experiment device

Abstract

The invention relates to the technical field of sensor devices, in particular to a sensor for a pipeline fluid-solid coupling simulation experiment device, which comprises a tail cylinder, a support cylinder is arranged at the inner end of the tail cylinder in a penetrating manner, a deceleration bag is sleeved on the outer surface of the support cylinder, and the deceleration bag is in surface contact fit with the inner wall of a pipeline after being inflated or pressed. A plurality of sensing devices are fixedly installed in the tail cylinder, a center cylinder is arranged at the inner end of the supporting cylinder in a penetrating mode, and through a linkage structure among the center shaft, the transmission sleeve, the stress cylinder and the locking block, the device can be automatically supported and locked on the inner wall of a pipeline after reaching a preset measuring point; the problem of overload impact or slippage generated in the locking process of a traditional rigid tight supporting structure is solved, when the center shaft continuously rotates and the locking block completes locking, the transmission sleeve is axially separated under the extrusion of the inclined face of the triangular push block, elastic receding is completed through the reset spring, and therefore continuous torque is prevented from directly acting on the locking structure, and the locking effect is improved. And mechanical meshing parts are effectively prevented from being damaged.

Description

Technical Field

[0001] This invention relates to the field of sensor device technology, specifically a sensor for a pipeline fluid-structure interaction simulation experiment device. Background Technology

[0002] During the operation of petrochemical, long-distance pipelines, water conservancy projects, and urban water supply and drainage networks, the fluid inside the pipeline will generate significant fluid-structure interaction with the pipe wall under high pressure, high flow velocity, and pulsating conditions. This interaction not only causes dynamic changes in flow field parameters but also further affects the vibration response and structural safety of the pipeline itself. Therefore, real-time monitoring of the instantaneous flow rate, pressure fluctuations, and flow field disturbance characteristics of the fluid medium on a pipeline dynamic experimental platform is of great significance for studying the fluid-structure interaction mechanism and establishing accurate numerical models.

[0003] In fluid-structure interaction simulation experiments, in order to analyze the effect of gas on the pipe wall under different pressure and flow rate conditions, it is usually necessary to place sensors at specific locations inside the pipe to obtain flow rate or velocity data in real time. However, most current pipe in-situ sensing devices can only complete the measurement at a single location. After completing the data acquisition of a certain area, the measurement process becomes cumbersome and has many limitations. Therefore, in order to realize the automatic switching and in-situ locking of the measuring point, this application proposes a sensor for a pipe fluid-structure interaction simulation experiment device. Summary of the Invention

[0004] The purpose of this invention is to provide a sensor for a pipeline fluid-structure interaction simulation experiment device to solve the problems mentioned in the background art.

[0005] To achieve the above objectives, the present invention provides the following technical solution: a sensor for a pipeline fluid-structure interaction simulation experiment device, comprising a tail cylinder, a support cylinder passing through the inner end of the tail cylinder, and a deceleration bladder fitted on the outer surface of the support cylinder. The deceleration bladder, after inflation or compression, forms a surface contact with the inner wall of the pipeline. Multiple sensing devices are fixedly installed inside the tail cylinder, and these sensing devices are evenly distributed in a ring along the circumferential direction, enabling distributed acquisition of flow rate or velocity signals at the same cross-section, thereby obtaining a more realistic distribution of the radial flow field. A central cylinder passes through the inner end of the support cylinder, and the central cylinder is connected to the tail cylinder by a soft rubber sleeve, forming a flexible buffer structure. Multiple rectangular holes are opened on the outer surface of the support cylinder, and locking blocks pass through each rectangular hole. The locking blocks extend outward and fit tightly against the inner wall of the pipeline, thus reliably fixing the radial position of the support cylinder, thereby limiting its continued displacement or rotational shift.

[0006] As a further embodiment of the present invention, a transmission cylinder is rotatably installed at the end of the central cylinder away from the tail cylinder. A push ring is fixedly sleeved on the outer surface of the transmission cylinder by bolts. Multiple triangular blocks are fixedly installed on the surface of the push ring. The triangular blocks correspond to each locking block, and the inclined surface of the triangular blocks contacts the tail end of the locking blocks to realize the synchronous external support and stable unfolding of the locking blocks, so that the sensor can be reliably supported and locked at the preset measuring point.

[0007] As a further embodiment of the present invention, two stepper motors are provided at the inner end of the central cylinder. The output end of the stepper motor near the push ring is fixedly connected to a central shaft. A transmission sleeve is slidably sleeved on the surface of the central shaft. The transmission sleeve is located inside the transmission cylinder. A force-bearing cylinder is movably installed inside the transmission cylinder. By setting two stepper motors at the inner end of the central cylinder, wherein the stepper motor near the push ring drives the central shaft to rotate and the transmission sleeve is slidably sleeved on the outside of the central shaft, the transmission force can be transmitted to the force-bearing cylinder inside the transmission cylinder through the transmission sleeve. This effectively converts the rotational displacement output by the motor into the axial or radial action required by the locking mechanism, thereby realizing the controllable drive of the tensioning mechanism.

[0008] As a further embodiment of the present invention, the transmission sleeve and the central shaft are connected by a return spring, so that the transmission sleeve is always pushed towards the force-bearing cylinder by the return spring when there is no external force interference, and maintains a close fit with the subsequent structure. Triangular push blocks are fixedly installed at the ends of the transmission sleeve and the force-bearing cylinder that are close to each other. By setting a return spring between the transmission sleeve and the central shaft, the transmission sleeve is always pushed towards the force-bearing cylinder by elastic force in the non-driving state, and maintains a close fit with the subsequent force-bearing structure. When the stepper motor drives the central shaft to rotate or displace, the transmission sleeve can transmit power to the force-bearing cylinder in a timely manner.

[0009] As a further embodiment of the present invention, multiple engagement rods are rotatably mounted on the inner end of the transmission cylinder. The multiple engagement rods are arranged in a ring along the circumference and are inclined relative to the central axis. A rack structure is fixedly installed at the end of each engagement rod. A toothed ring is fixedly fixed on the outer surface of the force-bearing cylinder, and the rack and toothed ring mesh with each other.

[0010] As a further embodiment of the present invention, an adjusting cylinder is fixedly installed at the inner end of the support cylinder, and an adjusting pipe is fixedly connected to the outer surface of the adjusting cylinder. The adjusting cylinder is connected to the deceleration bag through a transmission pipe. A stabilizing cover is fixedly installed at the end of the support cylinder away from the adjusting cylinder. By setting an adjusting cylinder at the inner end of the support cylinder and establishing a transmission connection structure between the adjusting pipe on the outer side of the adjusting cylinder and the deceleration bag, the gas state inside the deceleration bag can be synchronously adjusted with the opening and closing action of the adjusting cylinder.

[0011] As a further embodiment of the present invention, an adjusting cover is rotatably mounted on the surface of the stabilizing cover, and both the stabilizing cover and the adjusting cover have rectangular holes for gas flow. The degree of overlap between the two rectangular holes can be changed by adjusting the rotation angle of the adjusting cover. By rotatably mounting the adjusting cover on the surface of the stabilizing cover and opening rectangular vent holes on both surfaces, the overlapping area of ​​the two holes can be changed by adjusting the rotation angle of the adjusting cover, thereby realizing graded throttling control of gas flow.

[0012] As a further embodiment of the present invention, a movable plug is sleeved on the inner end of the adjusting tube. When the movable plug moves downward, it draws air from inside the deceleration bag. A balance bar is fixedly connected to the bottom end of the movable plug. A spool is rotatably installed on the inner end of the adjusting cylinder. A traction line is wound on the surface of the spool. The end of the traction line is fixedly connected to the end of the balance bar.

[0013] As a further embodiment of the present invention, a support ring is fixedly sleeved on the outer surface of the support cylinder, and multiple extension rods are uniformly rotatably installed on the outer side of the support ring along the circumferential direction. One end of each extension rod is rotatably installed with an abutment wheel for fitting against the inner wall of the pipe, and the other end is rotatably installed with a transmission rod. The end of the transmission rod is movably connected to the support ring.

[0014] Compared with the prior art, the beneficial effects of the present invention are: 1. This invention, through the linkage structure between the central shaft, transmission sleeve, force-bearing cylinder, and locking block, enables the device to automatically tighten and lock onto the inner wall of the pipe after reaching the preset measurement point. This avoids the overload impact or slippage problems caused by the traditional rigid tightening structure during the locking process. Furthermore, when the central shaft continues to rotate and the locking block has completed locking, the transmission sleeve achieves axial separation under the inclined surface extrusion of the triangular push block, and completes elastic relief through the return spring, thereby preventing continuous torque from directly acting on the locking structure and effectively avoiding damage to the mechanical meshing components. 2. The adjusting cover and the stabilizing cover of the present invention adopt an interlaced rectangular hole structure. By adjusting the relative position of the two, the throttling control of the pipeline gas is achieved. When the device is in the unlocking and moving stage, the internal gas pressure pushes the central cylinder to move, while the gas inside the deceleration bag is simultaneously extracted to form a flexible buffer, thereby making the moving speed of the central cylinder controllable and avoiding positioning errors or structural damage caused by rapid impact. Attached Figure Description

[0015] Figure 1 This is a schematic diagram of the structure of a pipeline sensor; Figure 2 This is a disassembled structural diagram of a pipeline sensor device. Figure 3 This is a schematic diagram of the internal structure of the support cylinder; Figure 4 This is a schematic diagram of the internal structure of the central cylinder; Figure 5 This is a structural diagram showing the internal structure of the central cylinder after disassembly. Figure 6 This is a schematic diagram of the internal structure of the transmission cylinder; Figure 7 This is a schematic diagram of the internal structure of the support cylinder; Figure 8 This is a schematic diagram of the internal structure of the support cylinder; Figure 9 This is a schematic diagram of the internal structure of the regulating cylinder; Figure 10 This is a structural diagram showing the positional relationship between the transmission rod and the contact plate. Figure 11 This is a diagram showing the status of the pipeline sensor inside the pipeline.

[0016] In the diagram: 1. Tailstock; 2. Locking block; 3. Deceleration bag; 4. Support cylinder; 5. Sensor device; 6. Soft rubber sleeve; 101. Extension rod; 102. Abutment wheel; 103. Support ring; 104. Transmission rod; 105. Limiting ring; 106. Abutment plate; 201. Center cylinder; 202. Push ring; 203. Limiting plate; 204. Center shaft; 205. Stepper motor; 206. Push cylinder; 207. Force-bearing seat; 301. Transmission cylinder; 302. Return spring; 303. Transmission sleeve; 304. Force-bearing cylinder; 305. Engaging rod; 401. Adjusting cylinder; 402. Adjusting pipe; 403. Transmission pipe; 404. Adjusting cover; 405. Stabilizing cover; 406. Movable plug; 407. Balance bar; 408. Traction line; 409. Thread reel. Detailed Implementation

[0017] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0018] Example 1: Please refer to Figure 1 - Figure 3A sensor for a pipeline fluid-structure interaction simulation experiment includes a tail cylinder 1. A support cylinder 4 passes through the inner end of the tail cylinder 1. A deceleration bladder 3 is fitted on the outer surface of the support cylinder 4. After being inflated or pressurized, the deceleration bladder 3 forms a surface contact with the inner wall of the pipeline. Its surface can provide sufficient friction to limit the axial displacement of the device, and also has a certain degree of airtightness, which can effectively suppress the interference of local fluid eddies on the sensing accuracy. Multiple sensing devices 5 are fixedly installed inside the tail cylinder 1 by bolts. The multiple sensing devices 5 are evenly distributed in a ring along the circumferential direction, so that the flow rate or velocity signal at the same cross section can be distributed to obtain a more realistic distribution of the radial flow field. Furthermore, the sensing device 5 integrates an integrated central control device for local synchronous processing and preliminary filtering of the raw signal, and transmits data to an external terminal via wired or wireless means to realize dynamic monitoring of real-time flow rate / velocity curves. A central cylinder 201 is inserted through the inner end of the support cylinder 4. The central cylinder 201 is connected to the tail cylinder 1 through a soft rubber sleeve 6 to form a flexible buffer structure. The non-rigid connection method can absorb displacement and angular deviation when the device passes through bends or pipe sections with different diameters. Even if the outer surface of the tail cylinder 1 comes into contact with the inner wall of the pipe, the deformation absorption effect of the soft rubber sleeve 6 can prevent hard friction or scratching of the inner wall of the pipe, thereby improving the adaptability and safety of the device in complex pipelines. Multiple rectangular holes are opened on the outer surface of the support cylinder 4. Locking blocks 2 are inserted in each rectangular hole. The locking blocks 2 extend outward and fit tightly against the inner wall of the pipe. At this time, the radial position of the support cylinder 4 is reliably fixed, thereby limiting its continued displacement or rotational offset.

[0019] In addition, the locking block 2 and the deceleration bag 3 together form a "double limiting" mechanism. The deceleration bag 3 provides axial friction fixation, and the locking block 2 provides radial support fixation, so that the entire measuring component can still maintain stable fit under the action of pulsating flow or transient pressure wave impact. When the pipe wall vibrates or pressure wave is transmitted, the central cylinder 201 can float slightly under the buffer of the soft rubber sleeve 6, thereby avoiding the direct transmission of external force to the sensor body, effectively reducing structural noise and installation disturbance during the test process, and improving the authenticity and repeatability of experimental data.

[0020] Example 2: Please refer to Figure 3 - Figure 6 A sensor for a pipeline fluid-structure interaction simulation experiment device, based on Embodiment 1, has a transmission cylinder 301 rotatably mounted on the end of the central cylinder 201 away from the tail cylinder 1. A push ring 202 is fixedly sleeved on the outer surface of the transmission cylinder 301 by bolts. Multiple triangular blocks are fixedly mounted on the surface of the push ring 202. The triangular blocks correspond to each locking block 2 and contact the tail end of the locking block 2 through the inclined surface of the triangular blocks. When the push ring 202 rotates, the triangular blocks use their inclined surfaces to push the locking blocks 2 to move. Two stepper motors 205 are provided at the inner end of the central cylinder 201. The output end of the stepper motor 205 away from the push ring 202 is fixedly connected to the push cylinder 206. A limit plate 203 is fixedly welded to the inner end of the central cylinder 201, and a force-bearing seat 207 is fixedly connected to the end of the limit plate 203 near the stepper motor 205. The surface of the push cylinder 206 is provided with multiple protrusions, and the surface of the force-bearing seat 207 is correspondingly provided with an inclined groove. The protrusions are located in the inclined groove. In this way, when the push cylinder 206 rotates under the drive of the stepper motor 205, the protrusions are forced to slide forward along the groove under the action of the inclined groove, thereby converting the rotational motion into the axial movement of the stepper motor 205 as a whole, so that the push ring 202 generates a smooth and reliable propulsive force. Specifically, to prevent the stepper motor 205 from rotating during axial movement, a rectangular groove is provided on its outer surface, and a corresponding rectangular strip is fixedly installed on the inner wall of the central cylinder 201. The rectangular strip is surface-limited and engaged in the rectangular groove, so that the stepper motor 205 is only allowed to perform linear reciprocating motion and cannot rotate.

[0021] like Figure 6 As shown, a central shaft 204 is fixedly connected to the output end of a stepper motor 205 near the push ring 202. A transmission sleeve 303 is slidably sleeved on the surface of the central shaft 204. The transmission sleeve 303 is located inside the transmission cylinder 301. A force-receiving cylinder 304 is movably installed inside the transmission cylinder 301. The transmission sleeve 303 and the central shaft 204 are connected by a return spring 302, so that the transmission sleeve 303 is always pushed towards the force-receiving cylinder 304 by the return spring 302 when there is no external force interference, and maintains a close fit with the subsequent structure. Triangular push blocks are fixedly installed at the ends of the transmission sleeve 303 and the force-receiving cylinder 304 that are close to each other, and the inclined surfaces of the two are arranged face to face. Under the elastic force of the return spring 302, the transmission sleeve 303 always pushes forward, so that the inclined surface of its own push block is reliably engaged with the push block on the force-receiving cylinder 304. When the stepper motor 205 drives the central shaft 204 and the transmission sleeve 303 to rotate, since the triangular push blocks of the two are always meshed and in contact, the transmission sleeve 303 can drive the force-receiving cylinder 304 to rotate synchronously, thereby further driving the push ring 202 to rotate in the locking direction.

[0022] like Figure 6 As shown, multiple engagement rods 305 are rotatably mounted on the inner end of the transmission cylinder 301. The multiple engagement rods 305 are arranged in a ring along the circumference and are inclined relative to the central axis 204. Each engagement rod 305 has a rack structure fixedly installed at its end. A toothed ring is fixedly fixed on the outer surface of the force-bearing cylinder 304. The rack and toothed ring mesh with each other to form a transmission engagement relationship. The engagement rods 305 and the transmission cylinder 301 are connected by torsion springs. Under the elastic force of the torsion springs, the engagement rods 305 are kept engaged with the toothed rings. It is worth noting that the biting rod 305 is installed at an angle, and its meshing direction with the toothed ring has a unidirectional force characteristic: when the force-receiving cylinder 304 rotates in the forward direction, the toothed ring pushes the biting rod 305 to receive force in its meshing direction, so that the inclined biting rod 305 transmits this torque to the transmission cylinder 301, thereby driving the transmission cylinder 301 to rotate synchronously and realize forward locking transmission. When the force-receiving cylinder 304 rotates in the reverse direction, the force direction of the biting rod 305 is opposite to its inclination angle. At this time, the toothed ring no longer applies an effective thrust to the biting rod 305, and the biting rod 305 turns into an idle or sliding state, so that the transmission cylinder 301 does not participate in the reverse drive, forming a unidirectional transmission effect.

[0023] like Figure 8 , Figure 9 As shown, an adjusting cylinder 401 is fixedly installed at the inner end of the support cylinder 4, and an adjusting pipe 402 is fixedly connected to the outer surface of the adjusting cylinder 401. The adjusting cylinder 401 is connected to the deceleration bag 3 through a transmission pipe 403. A stabilizing cover 405 is fixedly installed at the end of the support cylinder 4 away from the adjusting cylinder 401. An adjusting cover 404 is rotatably installed on the surface of the stabilizing cover 405. The adjusting cover 404 is sleeved on the outer surface of the central shaft 204. A rectangular groove is provided on the central shaft 204. A rectangular block that matches the adjusting cover 404 is fixedly provided on the inner wall of the adjusting cover 404, so that the adjusting cover 404 can maintain its posture synchronously with the central shaft 204 but can rotate independently, thereby ensuring that it will not produce radial sway during operation. Furthermore, both the stabilizing cover 405 and the adjusting cover 404 have rectangular holes for gas flow. By adjusting the rotation angle of the cover 404, the degree of overlap between the two rectangular holes can be changed, thereby controlling the effective opening area of ​​the air intake channel and achieving precise adjustment of air flow. Under a constant air pressure, the smaller the air flow, the greater the air thrust on the stabilizing cover 405. The inner end of the regulating tube 402 is fitted with a movable plug 406. When the movable plug 406 moves downward, it draws air from inside the deceleration bag 3. The bottom end of the movable plug 406 is fixedly connected to a balance bar 407. The inner end of the regulating cylinder 401 is rotatably mounted with a spool 409. A traction line 408 is wound around the surface of the spool 409. The end of the traction line 408 is fixedly connected to the end of the balance bar 407. The spool 409 is fitted on the outer surface of the central shaft 204 and rotates or moves axially synchronously with the central shaft 204. However, due to the flexible transmission characteristics of the traction line 408 and the reasonable design of the winding direction, its axial movement will not directly apply additional tension to the balance bar 407, thereby ensuring that the air conditioning device is not disturbed during the locking mechanism operation and realizing the non-interference between air pressure control and mechanical locking action.

[0024] like Figure 2 , Figure 10 , Figure 11As shown, a support ring 103 is fixedly sleeved on the outer surface of the support cylinder 4. Multiple extension rods 101 are evenly rotatably installed on the outer side of the support ring 103 along the circumferential direction. One end of the extension rod 101 is rotatably installed with an abutment wheel 102 for adhering to the inner wall of the pipe, and the other end is rotatably installed with a transmission rod 104. The end of the transmission rod 104 is movably connected to the support ring 103. The extension rod 101 and the support ring 103 are connected by a torsion spring (not shown in the figure). Under the elastic force of the torsion spring, the abutment wheel 102 always remains in contact with the inner wall of the pipe. Therefore, when transitioning from a thin pipe to a thick pipe, the abutment wheel 102 can always maintain contact with the inner wall of the pipe. A limiting ring 105 for forming a secondary limiting structure is sleeved on the outer side of the support ring 103. Multiple abutment plates 106 are rotatably mounted on the surface of the limiting ring 105. The abutment plates 106 abut against the outer side of the transmission rod 104 and are located inside the deceleration bladder 3. When the abutment wheel 102 deflects due to the change in pipe diameter, the transmission rod 104 first pushes the abutment plates 106 against the deceleration bladder 3, so that the deceleration bladder 3 is subjected to uniform compression load, thereby effectively avoiding the transmission rod 104 from generating concentrated shear force on the deceleration bladder 3 and preventing the deceleration bladder 3 from being damaged due to overload.

[0025] The working principle of this invention is: In use, the invention is placed inside a simulated experimental pipe, and the pipe begins to simulate the state of real gas passing through. At this time, the stepper motor 205 near the push ring 202 drives the central shaft 204 to rotate. The central shaft 204 drives the force-receiving cylinder 304 to rotate through the transmission sleeve 303. Then, the force-receiving cylinder 304 drives the transmission cylinder 301 to rotate through the biting rod 305. At this time, the push ring 202 will push the locking block 2 under the action of the triangular block. Finally, the locking block 2 is in close contact with the inner wall of the pipe and is locked at the predetermined measurement point of the pipe. Since the locking block 2 has been in contact with the inner wall of the pipe, it cannot move further, so the force-receiving cylinder 304 cannot continue to rotate. At this time, even if the transmission sleeve 303 continues to rotate under the drive of the central shaft 204, the triangular push block between it and the force-bearing cylinder 304 will be forced to separate axially due to the pressure of the inclined plane. The transmission sleeve 303 will retreat along the direction of the central shaft 204 and compress the reset spring 302. Then, when the external force is eliminated or the motor reverses during the unlocking phase, the reset spring 302 will push the transmission sleeve 303 back to its original position, so that the two will mesh again and complete an automatic reset process. Since the central shaft 204 is in a continuous rotating state, the rectangular hole on the surface of the adjusting cover 404 corresponds to the rectangular hole on the surface of the stabilizing cover 405, and the gas will flow out from the rectangular hole on the surface of the adjusting cover 404. At this time, the sensing device 5 will collect relevant data of the current position in the pipeline. The stepper motor 205 on the side away from the push ring 202 drives the push cylinder 206 to rotate. At this time, under the action of the force seat 207, the push cylinder 206 causes the stepper motor 205 to start moving away from the limit plate 203. As the stepper motor 205 starts to move, the central shaft 204 also starts to move. At this time, the spring travel between the transmission sleeve 303 and the central shaft 204 becomes shorter, and the transmission sleeve 303 will be subjected to a greater thrust. This restricts the axial movement space of the transmission sleeve 303. At this time, the rotational force of the central shaft 204 can be directly transmitted to the locking block 2, without worrying about the connection between the transmission sleeve 303 and the force cylinder 304 being disconnected. When a position change is required, the central shaft 204 reverses. At this time, the rectangular holes on the surfaces of the adjusting cover 404 and the stabilizing cover 405 intersect, preventing gas from passing through. This pushes the adjusting cover 404, causing the gas pressure to move the central cylinder 201. Simultaneously, the rotation of the central shaft 204 drives the sheave 409 to rotate. The rotation of the sheave 409 pulls the movable plug 406 through the traction line 408. As the movable plug 406 moves, it draws air from the deceleration chamber 3, but the deceleration chamber 3 remains in contact with the inner wall of the pipe to ensure airtightness. However, because the air inside the deceleration chamber 3 is reduced, the pressure on the inner wall of the pipe is reduced, ensuring that the support cylinder 4 moves neither too fast nor too slow. After moving to the next detection point, the stepper motor 205 drives the central shaft 204 to rotate. Then, the locking block 2 continues to be in contact with the inner wall of the pipe, allowing gas to continue to pass through the rectangular holes on the surface of the adjusting cover 404, and this process repeats.

[0026] The above are merely preferred embodiments of the present invention, but the scope of protection of the present invention is not limited thereto. Any equivalent substitutions or modifications made by those skilled in the art within the scope of the technology disclosed in the present invention, based on the technical solution and inventive concept of the present invention, should be covered within the scope of protection of the present invention.

Claims

1. A sensor for a pipeline fluid-structure interaction simulation experimental device, comprising a tail cylinder (1), characterized in that: The inner end of the tail cylinder (1) is provided with a support cylinder (4), and the outer surface of the support cylinder (4) is fitted with a deceleration bladder (3). After the deceleration bladder (3) is inflated or pressurized, it forms a surface contact with the inner wall of the pipe. Multiple sensing devices (5) are fixedly installed inside the tail cylinder (1). The multiple sensing devices (5) are evenly distributed in a ring along the circumferential direction, so that the flow rate or velocity signal at the same cross section can be collected in a distributed manner, thereby obtaining a more realistic distribution of the radial flow field. The inner end of the support cylinder (4) is provided with a central cylinder (201). The central cylinder (201) is connected to the tail cylinder (1) through a soft rubber sleeve (6) to form a flexible buffer structure. Multiple rectangular holes are opened on the outer surface of the support cylinder (4). Locking blocks (2) are inserted in each rectangular hole. The locking blocks (2) extend outward and fit tightly with the inner wall of the pipe. At this time, the radial position of the support cylinder (4) is reliably fixed, thereby limiting its continued displacement or rotational offset.

2. The sensor for a pipeline fluid-structure interaction simulation experimental device according to claim 1, characterized in that: A transmission cylinder (301) is rotatably mounted on the end of the central cylinder (201) away from the tail cylinder (1). A push ring (202) is fixedly sleeved on the outer surface of the transmission cylinder (301) by bolts. Multiple triangular blocks are fixedly mounted on the surface of the push ring (202). The triangular blocks correspond to each locking block (2) and contact the tail end of the locking block (2) through the inclined surface of the triangular blocks. When the push ring (202) rotates, the triangular blocks use their inclined surfaces to push the locking block (2) to move.

3. The sensor for a pipeline fluid-structure interaction simulation experimental device according to claim 2, characterized in that: The inner end of the central cylinder (201) is provided with two stepper motors (205). The output end of the stepper motor (205) near the push ring (202) is fixedly connected to a central shaft (204). A transmission sleeve (303) is slidably sleeved on the surface of the central shaft (204). The transmission sleeve (303) is located inside the transmission cylinder (301). A force-bearing cylinder (304) is movably installed inside the transmission cylinder (301).

4. The sensor for a pipeline fluid-structure interaction simulation experimental device according to claim 3, characterized in that: The transmission sleeve (303) is connected to the central shaft (204) by a return spring (302), so that the transmission sleeve (303) is always pushed towards the force-bearing cylinder (304) by the return spring (302) when there is no external force interference, and maintains a close fit with the subsequent structure. Triangular push blocks are fixedly installed at the ends of the transmission sleeve (303) and the force-bearing cylinder (304) that are close to each other. Under the elastic force of the return spring (302), the transmission sleeve (303) always pushes forward, so that the inclined surface of its own push block is reliably fitted with the push block on the force-bearing cylinder (304).

5. The sensor for a pipeline fluid-structure interaction simulation experimental device according to claim 4, characterized in that: The inner end of the transmission cylinder (301) is rotatably mounted with multiple biting rods (305). The multiple biting rods (305) are arranged in a ring along the circumference and are inclined relative to the central axis (204). Each biting rod (305) has a rack structure fixedly installed at its end. The outer surface of the force-bearing cylinder (304) is correspondingly fixed with a toothed ring, and the rack and toothed ring mesh with each other.

6. The sensor for a pipeline fluid-structure interaction simulation experimental device according to claim 1, characterized in that: An adjusting cylinder (401) is fixedly installed at the inner end of the support cylinder (4), and an adjusting pipe (402) is fixedly connected to the outer surface of the adjusting cylinder (401). The adjusting cylinder (401) is connected to the deceleration bag (3) through a transmission pipe (403). A stabilizing cover (405) is fixedly installed at the end of the support cylinder (4) away from the adjusting cylinder (401).

7. The sensor for a pipeline fluid-structure interaction simulation experimental device according to claim 6, characterized in that: An adjusting cover (404) is rotatably mounted on the surface of the stabilizing cover (405), and both the stabilizing cover (405) and the adjusting cover (404) have rectangular holes for gas flow. The degree of overlap between the two rectangular holes can be changed by adjusting the rotation angle of the adjusting cover (404). Under a constant air pressure, the smaller the air flow, the greater the air thrust on the stabilizing cover (405).

8. The sensor for a pipeline fluid-structure interaction simulation experimental device according to claim 7, characterized in that: The inner end of the regulating tube (402) is fitted with a movable plug (406). When the movable plug (406) moves downward, it will draw air from the deceleration bag (3). The bottom end of the movable plug (406) is fixedly connected to a balance bar (407). The inner end of the regulating cylinder (401) is rotatably mounted with a spool (409). The surface of the spool (409) is wound with a traction line (408). The end of the traction line (408) is fixedly connected to the end of the balance bar (407).

9. The sensor for a pipeline fluid-structure interaction simulation experimental device according to claim 8, characterized in that: A support ring (103) is fixedly sleeved on the outer surface of the support cylinder (4). Multiple extension rods (101) are evenly rotated on the outer side of the support ring (103) in the circumferential direction. One end of the extension rod (101) is rotatably mounted with an abutment wheel (102) for fitting against the inner wall of the pipe, and the other end is rotatably mounted with a transmission rod (104). The end of the transmission rod (104) is movably connected to the support ring (103).

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