Hydroelectric generating set guide vane opening dynamic deviation monitoring and self-adaptive correction device and system

Abstract

The invention discloses a dynamic deviation monitoring and self-adaptive correction device and system for the opening degree of a guide vane of a hydroelectric generating set. The device comprises a guide vane and a shaft rod mechanism, a star-shaped tooth groove is formed in the guide vane, star-shaped angle teeth matched with the tooth groove are arranged on the shaft rod mechanism, the angle teeth are located in the tooth groove, a plurality of gaps are formed between the angle teeth and the tooth groove, and a plurality of buffer adjusting assemblies located in the gaps are arranged between the guide vane and the shaft rod mechanism. And the end part of the guide vane and the end part of the shaft rod mechanism are connected with the guide vane end cover. The system comprises the guide vane control connecting rod and further comprises the device. The guide vane structure has the beneficial effects that through the synergistic effect of the detachable guide vane structure, the shaft rod mechanism installed in a clearance mode and the buffer adjusting assembly, the guide vane opening deviation is monitored in real time and adjusted in a self-adaptive mode, and the problems that a traditional guide vane structure is difficult to maintain, poor in impact resistance and insufficient in monitoring precision are solved; the maintainability and the impact resistance of the guide vane structure are improved.

Description

Technical Field

[0001] This application belongs to the technical field of hydropower equipment, specifically relating to a device and system for monitoring and adaptively correcting the dynamic deviation of the guide vane opening of a hydropower unit. Background Technology

[0002] As a core equipment for clean energy conversion, the operational efficiency and stability of hydropower units are of paramount importance. The guide vane mechanism, especially the movable guide vanes, is a key component for achieving precise flow regulation and ensuring efficient and stable turbine operation. However, traditional guide vane structures face significant challenges during long-term service: First, the guide vane body and its transmission mechanisms (such as connecting rods, crank arms, and control rings) often experience issues due to hydraulic pulsation, silt abrasion, cavitation, and manufacturing / installation errors, leading to guide vane journal jamming, end-face seal failure, and accelerated wear at critical hinge points. This not only increases operating torque but also easily causes asynchronous guide vane opening, sluggish action, or even jamming, severely affecting the speed and accuracy of unit regulation. Second, guide vane profile design often focuses on efficiency at specific operating points, making it difficult to adapt to the high-efficiency operation requirements under wide variations in head and flow. Furthermore, under complex hydraulic excitation, it is prone to vibration, threatening unit safety. Therefore, the inherent limitations of existing guide vane structures in improving reliability, reducing hydraulic losses, suppressing vibration, and adapting to complex operating conditions have become a technical bottleneck restricting further performance improvements of hydropower units.

[0003] Meanwhile, the technology for precise monitoring and dynamic correction of guide vane opening also has shortcomings. Current hydropower stations cannot directly and in real-time perceive the true spatial position of each guide vane, making it difficult to accurately reflect synchronization deviations between guide vanes and potential deformation or wear of the guide vane body. More importantly, existing monitoring systems are mostly limited to opening display and over-limit alarms, lacking the ability to deeply couple and analyze real-time, high-precision opening information with unit operating conditions. This prevents them from proactively identifying abnormal guide vane conditions (such as jamming, asynchrony, or slight deformation) and implementing online dynamic correction and compensation. Adjusting the control system based on inaccurate opening signals not only reduces efficiency but may also induce increased pressure pulsation, excessive unit vibration, and even amplified hydraulic oscillations. Therefore, it is urgent to overcome the limitations of existing guide vane opening monitoring technology, develop high-precision, real-time dynamic monitoring methods, and construct a closed-loop control system with intelligent analysis and adaptive correction capabilities to fundamentally address the negative impact of inaccurate guide vane conditions on unit performance and safety. Summary of the Invention

[0004] The purpose of this application is to provide a device and system for monitoring and adaptively correcting the dynamic deviation of the guide vane opening of a hydroelectric generator, which can improve the maintainability and shock resistance of the guide vane structure, realize real-time monitoring and adaptive correction of dynamic deviation, and improve the operating efficiency and stability of the unit. It solves the inherent limitations of existing guide vane structures in improving reliability, reducing hydraulic loss, suppressing vibration and adapting to complex working conditions, as well as the shortcomings of existing precise monitoring and dynamic correction technologies for guide vane opening.

[0005] The objective of this application is achieved through the following technical solution: A device for monitoring and adaptively correcting the dynamic deviation of guide vane opening in a hydroelectric generator includes a guide vane and a shaft mechanism. The guide vane is provided with star-shaped toothed grooves, and the shaft mechanism is provided with star-shaped angular teeth that match the toothed grooves. The angular teeth are located in the toothed grooves and form several gaps between them. Several buffer adjustment components located in the gaps are provided between the guide vane and the shaft mechanism. The ends of the guide vane and the shaft mechanism are both connected to the guide vane end caps.

[0006] Furthermore, the tooth grooves and corner teeth are matched in a five-pointed star shape.

[0007] Furthermore, the guide vane includes two guide vane sections, each with a toothed groove. The toothed grooves on the two guide vane sections are joined together to form a toothed groove, and the side of the guide vane section is provided with an anti-scratch film.

[0008] Furthermore, the guide vane section has slots on both sides, and a connector is provided between the slots on the same side. The two ends of the connector are respectively inserted into the slots of the two guide vane sections, and the connector is connected to the guide vane section by bolts.

[0009] Furthermore, the shaft mechanism includes a shaft portion, on which angular teeth are provided.

[0010] Furthermore, the buffer adjustment assembly includes a first connector, with dampers connected to both ends of the first connector, and the dampers at both ends respectively hinged to a second connector. The lower parts of the second connectors at both ends are respectively connected to the upper parts of the second support hydraulic cylinders. The second support hydraulic cylinders at both ends are respectively hinged to the lower ends of the first connectors. The upper parts of the second connectors at both ends are provided with a first monitoring buffer head that contacts the guide vane, and the lower parts of the second support hydraulic cylinders at both ends are provided with a second monitoring buffer head that contacts the shaft mechanism.

[0011] Furthermore, the first monitoring buffer head includes a shock absorber, a buffer plate, and a piezoelectric thin film sensor. Shock absorbers are respectively provided on the second connecting parts at both ends, and a buffer plate is connected between the shock absorbers at both ends. A piezoelectric thin film sensor is provided on the upper surface of the buffer plate. The second monitoring buffer head includes a shock absorber, a buffer plate, and a piezoelectric thin film sensor. Shock absorbers are respectively provided on the second supporting hydraulic cylinders at both ends, and a buffer plate is connected between the shock absorbers at both ends. A piezoelectric thin film sensor is provided on the lower surface of the buffer plate.

[0012] Furthermore, the shock absorber includes a support sleeve, on which a telescopic damping rod is provided, and on which a piston is provided inside the support sleeve. The inside of the support sleeve is divided into an upper oil chamber and a lower oil chamber by the piston. The upper oil chamber and the lower oil chamber are connected by an oil delivery pipe. The support sleeve is fitted on the bearing sleeve, and a buffer chamber connected to the lower oil chamber is formed between the support sleeve and the bearing sleeve.

[0013] Furthermore, the support sleeve is equipped with an inlet solenoid valve that connects the buffer chamber and the lower oil chamber. The buffer chamber is connected to the oil pump through a pipeline, the oil pump is connected to the reversing valve through a pipeline, and the reversing valve is connected to the upper oil chamber and the lower oil chamber through pipelines respectively.

[0014] A dynamic deviation monitoring and adaptive correction system for guide vane opening of a hydropower unit includes a guide vane control linkage and the aforementioned dynamic deviation monitoring and adaptive correction device for guide vane opening of the hydropower unit. The guide vane control linkage is connected to a shaft mechanism and to a guide vane control hydraulic cylinder. Several guide vane control hydraulic cylinders are connected to a control ring, and the control ring is connected to a piston cylinder.

[0015] The beneficial effects of this application are as follows: Through the synergistic effect of the detachable guide vane structure, the gap-mounted shaft mechanism, and the buffer adjustment component, the guide vane opening deviation is monitored in real time and adjusted adaptively. This solves the problems of difficult maintenance, poor shock resistance, and insufficient monitoring accuracy of traditional guide vane structures. It has the advantages of improving the maintainability and shock resistance of the guide vane structure, while realizing real-time monitoring and adaptive correction of dynamic deviation, thereby improving the unit's operating efficiency and stability.

[0016] The aforementioned main solution and its various further alternatives can be freely combined to form multiple solutions, all of which are solutions that can be adopted and are claimed in this application; furthermore, the (non-conflicting alternatives) can also be freely combined with each other and with other alternatives. Those skilled in the art, after understanding the solution of this application, will realize from the prior art and common general knowledge that there are many combinations, all of which are technical solutions to be protected by this application, and will not be exhaustively listed here. Attached Figure Description

[0017] Figure 1 This is a schematic diagram of the device in this application (with the guide vane end cover installed).

[0018] Figure 2 This is a schematic diagram of the device in this application (with the guide vane end cover removed).

[0019] Figure 3 This is a schematic diagram of the guide vane structure of this application.

[0020] Figure 4 This is a structural schematic diagram of the shaft mechanism of this application.

[0021] Figure 5 This is a schematic diagram of the structure of the buffer adjustment component of this application.

[0022] Figure 6 This is a structural appearance drawing of the shock absorber in this application.

[0023] Figure 7 This is a structural cross-sectional view of the shock absorber in this application.

[0024] Figure 8 This is a schematic diagram of the guide vane end cap of this application.

[0025] Figure 9 This is a schematic diagram of the system structure of this application.

[0026] In the diagram: 1-Guide vane, 101-Guide vane section, 102-Groove, 103-Anti-scratch film, 104-Slot, 105-Plug-in seat, 106-Guide vane cover bolt hole; 2-Shaft mechanism, 201-Shaft section, 202-Shaft bolt hole, 203-Angle tooth; 3-Buffer adjustment assembly, 301-First connector, 302-Damper, 303-Second connector, 304-First support hydraulic cylinder, 305-Second support hydraulic cylinder, 306-Shock absorber, 3061-Support sleeve, 3 062-Bearing sleeve, 3063-Shock absorber rod, 3064-Oil delivery pipe, 3065-Piston, 3066-Guide sleeve, 3067-Buffer cavity, 3068-Inlet solenoid valve, 3069-Oil pump, 3070-Directional valve, 307-Buffer plate, 308-Piezoelectric film sensor; 4-Guide vane end cover, 401-Shaft hole, 402-Angle tooth hole, 403-Guide vane end cover bolt hole; 5-Piston cylinder, 6-Control ring, 7-Guide vane control linkage, 8-Guide vane control hydraulic cylinder. Detailed Implementation

[0027] In existing technologies, hydropower unit guide vanes have long faced the problem of insufficient adjustment accuracy due to dynamic deviations. Traditional guide vane structures suffer from journal jamming, seal failure, and wear at hinge points, leading to asynchronous opening and sluggish operation. Existing monitoring systems are limited to opening display and alarm functions, unable to perceive the actual spatial position of the guide vanes in real time, and lack dynamic correction capabilities. Control systems rely on misalignment signals for adjustment, which can easily cause pressure pulsations and excessive vibration, threatening the safe and stable operation of the unit.

[0028] To address the aforementioned issues and the challenge of real-time monitoring and compensation for guide vane dynamic deviations, the first consideration is to establish an adjustable physical clearance between the guide vane and the shaft mechanism. By analyzing the energy transfer path of the guide vane motion, a buffer adjustment component with both monitoring and execution functions is integrated at the clearance. Furthermore, a modular assembly system is constructed based on a detachable structural design concept to reduce maintenance difficulty. Ultimately, a solution is formed that absorbs deviations through mechanical clearance, adjusts hydraulic damping in real time, and implements multi-component collaborative closed-loop control.

[0029] The following non-limiting embodiments are used to illustrate this application.

[0030] Example 1 refer to Figures 1-8 As shown, a device for monitoring and adaptively correcting the dynamic deviation of the guide vane opening of a hydroelectric generator includes a guide vane 1, a shaft mechanism 2, a buffer adjustment assembly 3, and a guide vane end cover 4.

[0031] The guide vane 1 has a star-shaped toothed groove 102, and the shaft mechanism 2 has star-shaped angle teeth 203 that match the toothed groove 102. The star-shaped toothed groove between the guide vane 1 and the shaft mechanism 2 can disperse the contact stress between the two and improve the transmission accuracy. The angle teeth 203 are located in the toothed groove 102 and form several gaps between them. By adjusting the size of these gaps, the physical position can be adjusted and compensated.

[0032] Several buffer adjustment components 3 are provided between the guide vane 1 and the shaft mechanism 2, located within the gap. These buffer adjustment components 3 are used for real-time monitoring and adaptive correction of the dynamic deviation between the guide vane 1 and the shaft mechanism 2. The ends of both the guide vane 1 and the shaft mechanism 2 are connected to the guide vane end cap 4, thus integrating the ends of the guide vane and the shaft mechanism 2 into a single unit. The toothed groove 102 and the angle tooth 203 are mutually matched pentagonal stars, which avoids significant manufacturing difficulties while ensuring a good fit between the guide vane 1 and the shaft mechanism 2.

[0033] The guide vane 1 is installed on the top cover and has a detachable structure for easy installation or maintenance. The shaft mechanism 2 is detachably connected to the guide vane 1 and forms a gap. The buffer adjustment component 3 is set at the gap for monitoring and adjustment. The guide vane end cover 4 is bolted to connect the guide vane 1 and the shaft mechanism 2 to form an integrated structure.

[0034] Guide vane 1 refers to the fluid control component installed on the turbine top cover. It can be implemented using a split-type modular structure for easy on-site disassembly and maintenance. Shaft mechanism 2 refers to the transmission component connecting guide vane 1 to the control system. It can be implemented using a shaft structure with bevel gears 203, and its installation clearance with guide vane 1 provides displacement space for dynamic adjustment. Buffer adjustment component 3 refers to a hydraulic damping device integrating monitoring and execution functions. It can be implemented using a combination of a multi-directional damper and a hydraulic cylinder, used to absorb kinetic energy and correct deviations. Guide vane end cap 4 refers to the connecting component that fixes guide vane 1 to the shaft. It can be implemented using a disc-shaped structure with shaft holes and bolt holes, ensuring connection rigidity while allowing the buffer component to function.

[0035] The guide vane 1 adopts a split, detachable structure, enabling quick assembly and disassembly via bolt connections, reducing maintenance difficulty. The installation gap between the shaft mechanism 2 and the guide vane 1 provides physical space for dynamic deviation adjustment, avoiding stress concentration caused by rigid connections. The buffer adjustment assembly 3 is located in the gap area and monitors the displacement deviation of the guide vane 1 in real time via built-in sensors. When an abnormal opening is detected, the hydraulic cylinder and damper work together to generate a counterforce for compensation and adjustment. The guide vane end cap 4 serves as the connection interface, ensuring a reliable connection between the shaft and the guide vane 1 while providing an installation reference surface for the buffer assembly. All components form a closed-loop control system. The buffer assembly feeds back the monitoring data to the control system in real time, driving the hydraulic actuator to complete dynamic correction.

[0036] Traditional guide vanes employ a monolithic cast structure and rigid connection, which cannot effectively absorb dynamic deviations and are difficult to maintain. This solution improves maintainability through a split guide vane design, utilizing the clearance space to arrange the buffer adjustment component 3 for real-time monitoring and active compensation. Existing technologies rely on a single position sensor to monitor the opening; this solution integrates a photoelectric encoder and a laser velocimeter at the shaft end to achieve simultaneous acquisition of multi-dimensional motion parameters. Traditional buffer devices only have unidirectional damping function; this solution's buffer component, through a combination of a multi-directional damper and a hydraulic cylinder, can adaptively absorb motion energy from different directions.

[0037] This solution effectively addresses the issue of insufficient adjustment accuracy caused by dynamic deviation of the guide vane 1. The detachable guide vane structure significantly reduces maintenance time, and the clearance space design provides a physical basis for dynamic adjustment. The buffer adjustment component 3 enables real-time monitoring and active compensation of opening deviation, improving the unit's operational stability. The modular assembly system enhances system maintainability, and multi-sensor collaborative monitoring ensures control accuracy. The coupling design of hydraulic damping and mechanical structure effectively absorbs vibration energy and extends the service life of key components.

[0038] The guide vane 1 includes a guide vane section 101, a toothed groove 102, an anti-scratch membrane 103, a slot 104, a connector 105, and a guide vane cover bolt hole 106. The guide vane 1 is formed by combining two guide vane sections 101 in half. Each guide vane section 101 has a toothed groove, which connects with the two sections to form the toothed groove 102. An anti-scratch membrane 103 is fixed to the side of each guide vane section 101 by bolts. The end face of each guide vane section 101 has a guide vane cover bolt hole 106, through which bolts are fitted to securely connect the guide vane section 101 to the guide vane end cover 4.

[0039] The guide vane section 101 refers to the guide vane 1 body being symmetrically divided into two independent parts along its axis. These parts can be machined separately using casting or forging processes and then assembled using locating pins and bolts. The toothed groove 102 refers to the toothed structure with alternating protrusions and recesses formed at the mating surface of the guide vane section 101. This can be formed using CNC milling or EDM machining and is used for multi-point meshing transmission with the shaft mechanism 2. The anti-scratch film 103 is an anti-wear protective layer covering the surface of the guide vane 1. This layer can be made of polyurethane elastomer or a ceramic composite coating and is fixed to the surface of the guide vane 1 using countersunk bolts. It is used to isolate the guide vane 1 body from direct contact with solid particles in the water flow.

[0040] Each of the two guide vane sections 101 has a slot 104 on both sides, and a connector 105 is provided between the slots 104 on the same side. The two ends of the connector 105 are respectively inserted into the slots 104 of the two guide vane sections 101, and the connector 105 is connected to the guide vane section 101 by bolts. The connector 105 adopts a U-shaped structure, and is inserted and locked through the two ends of the U-shape, and fixedly connected through the middle of the U-shape.

[0041] After being machined separately, the guide vane section 101 is pre-positioned through the insertion and engagement between the slot 104 and the connector 105, and then fastened with bolts. The five-star toothed groove structure 102 formed between the guide vane sections 101 engages with the five-star angle teeth 203 of the shaft mechanism 2 during transmission, effectively dispersing contact stress and improving transmission accuracy. The anti-scratch membrane 103 is fixed to the upstream and downstream surfaces of the guide vane 1 with bolts. In case of localized wear or cavitation damage, only the bolts in the corresponding area need to be removed to replace the protective layer, without the need to completely remove the guide vane 1. Compared to traditional rectangular toothed grooves, the geometric configuration of the five-star toothed groove 102 increases the number of contact points and optimizes the stress distribution path, enabling the guide vane 1 to maintain stable synchronization accuracy during frequent opening and closing.

[0042] Traditional guide vanes employ a monolithic cast structure, requiring complete hoisting for installation and maintenance. In contrast, the modular guide vane section 101 allows for disassembly and assembly in confined spaces, significantly reducing construction difficulty. Conventional guide vane surface protection often utilizes a hard alloy overlay, necessitating cutting and re-welding during maintenance. The removable anti-scratch membrane 103 design enables rapid replacement of the protective layer. Existing guide vane drive tooth grooves are mostly rectangular or trapezoidal, prone to root fracture under long-term alternating loads. The five-star tooth groove design effectively reduces single-tooth load through multi-tooth contact, extending the lifespan of the transmission structure.

[0043] This solution enables rapid disassembly and maintenance of the guide vane 1, reducing downtime. The split structure and five-star toothed groove 102 design improve the synchronization accuracy of the multi-guide vane 1 linkage control, and the removable anti-scratch film 103 effectively reduces the surface wear rate of the guide vane 1, avoiding damage to the guide vane 1 body due to the failure of the protective layer.

[0044] The guide vane section 101 has a slot 104. The two guide vane sections 101, after mating, are installed in the slot 104 via a connector 105 and secured with bolts. The slot 104 is a groove structure along the mating edge of the guide vane section 101, which can be formed by machining or casting. Its cross-sectional shape is, for example, rectangular, trapezoidal, or dovetail-shaped, used to form a geometric fit with the connector 105. The connector 105 is a protruding component that matches the shape of the slot 104. It can be made of high-strength alloy steel or composite material, and its size is slightly smaller than the slot 104 to allow for assembly clearance. During installation, it is embedded into the slot 104 through an interference fit or clearance fit, thus limiting the lateral displacement of the guide vane section 101.

[0045] During the docking assembly of the guide vane segments 101, the connector 105 is pre-installed in the slot 104 of one of the guide vane segments 101. When the two guide vane segments 101 are docked, the connector 105 is inserted into the corresponding slot 104 of the other guide vane segment 101, forming a mechanical fitting constraint, forcing the guide vane segment 101 to complete positioning along a preset trajectory. The geometric fit between the slot 104 and the connector 105 eliminates horizontal installation deviations of the guide vane segment 101, ensuring precise mating of the mating surface grooves 102. Subsequently, bolts are inserted into the pre-drilled bolt holes in the guide vane segment 101 and preload is applied, making the mating surfaces fit tightly together, further suppressing minor displacements caused by vibration or hydraulic impact. The connector 105 and the bolt form a dual constraint mechanism: the connector 105 undertakes the main positioning and shear load resistance functions, while the bolt provides mechanical support against torsion and separation. The two work together to improve the connection stiffness of the guide vane segment 101.

[0046] Traditional guide vane assembly relies solely on bolts for direct fastening, lacking a positioning reference. This makes it prone to misalignment of the toothed groove 102 due to assembly errors, and the bolts are susceptible to loosening under long-term shear forces. This solution, through the geometric constraint design of the slot 104 and the insertion seat 105, achieves self-alignment of the guide vane assembly 101 during the assembly stage. This reduces the skill requirements for operators and distributes the stress on the bolts, avoiding the risk of failure at a single connection point.

[0047] This solution effectively solves the connection instability problem caused by installation errors during the docking of the guide vane section, improving the assembly accuracy and structural integrity of the guide vane section. The mating design of the slot 104 and the plug-in seat 105 allows the guide vane section 101 to automatically correct positional deviations during assembly, ensuring precise meshing of the toothed grooves 102 and avoiding stress concentration caused by misalignment. After the plug-in seat 105 completes the initial positioning, the bolt connection applies a tightening force, forming redundant constraints, significantly reducing the risk of connection loosening due to vibration or hydraulic pulsation during guide vane operation, thereby ensuring the synchronicity and stability of the guide vane movement.

[0048] The shaft mechanism 2 includes a shaft section 201, on which angular teeth 203 are provided. The shaft section 201 is the transmission component connecting the guide vane 1 and the control mechanism. It can be forged from high-strength alloy steel, and its end flange structure is rigidly connected to the guide vane end cover 4 via bolts, ensuring the stability of mechanical load transmission. The angular teeth 203 are plug-in components with a polygonal star-shaped cross-section, specifically made of surface-hardened 42CrMo alloy steel. Their geometry forms a clearance fit with the five-star toothed grooves 102 of the guide vane section 101, achieving dual positioning with the guide vane end cover 4 through the shaft bolt holes 202 after plugging. The photoelectric encoder is an angular displacement sensor based on the grating principle, specifically an absolute multi-turn encoder. Its rotor is directly mounted at the end of the shaft section 201, achieving real-time angle measurement by acquiring high-frequency pulse signals of the shaft rotation angle. A laser Doppler velocimeter is a linear velocity sensor based on the principle of optical interference. Specifically, it can be implemented by using a 532nm wavelength laser source in conjunction with a high-speed photodetector. Its measurement beam is projected onto the rotating surface along the shaft 201 axis, and the instantaneous rotational speed of the shaft is inverted through Doppler frequency shift.

[0049] The angle teeth 203 and the tooth groove 102 form a clearance fit, eliminating the assembly clearance after the guide vane end cover 4 bolts are tightened, ensuring the synchronous rotation of the shaft 201 and the guide vane 1. A photoelectric encoder directly measures the end angle of the shaft, eliminating the angle transmission error introduced by traditional linkage transmission mechanisms. A laser Doppler velocimeter synchronously measures the linear velocity of the shaft surface, obtaining the angle change trend through integration. After time synchronization processing of the two sensor data, a dynamic kinematic model of the guide vane 1 opening can be constructed to identify speed fluctuations or angle lag caused by guide vane 1 jamming. The five-star angle teeth and five-star tooth grooves form five contact angles and ten contact surfaces in the circumferential direction. Buffer adjustment components 3 are arranged at the gaps of each contact surface, monitoring the pressure distribution of the contact surfaces in real time during shaft rotation. Three-dimensional monitoring of the dynamic deviation of the guide vane 1 is achieved through the coordinated data acquisition of the ten sets of buffer adjustment components 3.

[0050] Traditional guide vane opening monitoring relies on a single angle sensor installed at the far end of the control loop, which cannot eliminate measurement errors caused by transmission chain backlash. This solution integrates a photoelectric encoder and a laser Doppler velocimeter at the end of the shaft, enabling direct measurement of the individual guide vane body and eliminating error interference from intermediate transmission links. In existing technologies, the five-star angular tooth structure is only used for mechanical positioning. This solution, through the multi-contact surface layout formed by the clearance fit between the five-star angular teeth 2 and the five-star tooth grooves, combined with the distributed arrangement of the buffer adjustment components 3, achieves multi-dimensional monitoring of the dynamic deviation of the guide vane 1.

[0051] This solution can acquire precise angle and rotational speed data of a single guide vane 1 in real time. By using dual-sensor fusion processing, it eliminates the inherent errors of a single measurement method and accurately identifies the minute angular deviations and speed fluctuations that occur in the initial stage of guide vane 1 jamming. The clearance fit structure between the five-star angular tooth 203 and the guide vane section 101 ensures mechanical rigidity while providing multiple contact surface monitoring points for the buffer adjustment component 3, realizing three-dimensional state perception of the dynamic deviation of guide vane 1, and providing a high-precision data foundation for subsequent adaptive correction.

[0052] The buffer adjustment assembly 3 is used to monitor the guide vane opening deviation and make adaptive adjustments during the monitoring process. Specifically, it includes a first connector 301, a damper 302, a second connector 303, a first support hydraulic cylinder 304, a second support hydraulic cylinder 305, a first monitoring buffer head, and a second monitoring buffer head.

[0053] The first connector 301 is located at the center of the component and is arranged laterally. The two ends of the first connector 301 are fixedly connected to the dampers 302, which are also arranged laterally. That is, there are two sets of dampers 302, which are installed at both ends of the first connector 301 in the lateral direction, and the dampers 302 provide a buffering effect.

[0054] The dampers 302 at both ends are hinged to the second connector 303. The second connector 303 is also arranged laterally, that is, there are two sets of the second connector 303, which are hinged to the dampers at both ends in the lateral direction, and the structural transition of forces in each direction is carried out through the second connector 303.

[0055] The lower parts of the second connecting parts 303 at both ends are fixedly connected to the upper parts of the second supporting hydraulic cylinders 305. The second supporting hydraulic cylinders 305 are arranged vertically, that is, there are two sets of second supporting hydraulic cylinders 305. The two sets of second supporting hydraulic cylinders 305 are arranged vertically at both ends of the component for vertical pressure adjustment.

[0056] The second support hydraulic cylinder 305 at both ends is hinged to the first support hydraulic cylinder 304 at the lower ends of the first connecting member 301. The first support hydraulic cylinder 304 is arranged obliquely, that is, there are two sets of the first support hydraulic cylinder 304. The two ends of the first support hydraulic cylinder 304 are respectively hinged to the first connecting member 301 and the second support hydraulic cylinder 305, and are used for oblique (including horizontal and vertical) pressure adjustment.

[0057] The upper part of the second connecting parts 303 at both ends is provided with a first monitoring buffer head, and the lower part of the second supporting hydraulic cylinders 305 at both ends is provided with a second monitoring buffer head. The monitoring buffer head has a buffering and shock absorption function, and can also monitor the force to determine the state of the guide vane.

[0058] The damper 302, the second connector 303, the first support hydraulic cylinder 304 and the second support hydraulic cylinder 305 are arranged symmetrically on the left and right sides along the first connector 301, forming a structural form in which the components are symmetrically subjected to force.

[0059] The first connector 301 is a core structural component used to connect the various actuators of the assembly. Specifically, it can be an I-beam forged from high-strength alloy steel, serving to transmit loads and coordinate the movements of various components. The damper 302 is an energy-absorbing device used to absorb impact energy. Specifically, it can be a twin-cylinder hydraulic damper with a hinged design at both ends that allows rotation around an axis, achieving multi-directional energy absorption.

[0060] The second support hydraulic cylinder 305 refers to a hydraulic actuator arranged vertically, specifically a double-acting piston hydraulic cylinder, which provides vertical support rigidity through telescopic movement. The first support hydraulic cylinder 304 refers to a symmetrically inclined hydraulic actuator, specifically a single-rod double-acting hydraulic cylinder, with the two sets of hydraulic cylinders forming an inclined support structure to distribute the load.

[0061] When pressure or displacement energy is generated during guide vane opening adjustment, the two sets of symmetrically inclined first support hydraulic cylinders 304 decompose the load into axial and lateral forces, dispersing the pressure transmission path through the extension and contraction deformation of the hydraulic cylinders. Two sets of horizontally mounted dampers 302 directly absorb energy in the main impact direction, while the hinged design allows the dampers 302 to rotate around the hinge point when deforming at the bearing end, thereby changing the energy absorption direction and covering the impact component in the non-horizontal direction. The second support hydraulic cylinder 305 provides rigid support in the vertical direction, forming a vertical support relationship with the second connecting member 303, suppressing vertical displacement of the structure. The synergistic effect of the inclined bracing structure, horizontal dampers, and vertical support constructs an energy absorption network in three-dimensional space, enabling impact energy from different directions to be dissipated through corresponding components, avoiding instability caused by local overload.

[0062] Traditional guide vane buffer devices mostly use springs or hydraulic dampers in a single direction, which can only absorb impact energy in a fixed direction and cannot adapt to multi-dimensional composite load conditions. In contrast, this solution combines a symmetrical bracing structure with a hinged damper, enabling energy in the horizontal, vertical, and inclined directions to be absorbed through the corresponding hydraulic actuators and dampers. At the same time, the hinged structure gives the damper the ability to adaptively adjust its direction, significantly expanding the dimensions and efficiency of energy absorption.

[0063] This solution effectively solves the structural instability problem caused by multi-directional energy impacts during guide vane opening adjustment. Through the synergistic effect of the inclined bracing structure decomposing the load path, the multi-directional damper absorbing the impact energy, and the vertical hydraulic cylinder providing rigid support, the three-dimensional stability control of the guide vane mechanism during dynamic adjustment is achieved. At the same time, the articulated damper design enhances the device's adaptability to impacts from different directions, ensuring the accuracy and reliability of the guide vane opening adjustment action.

[0064] The first monitoring buffer head includes a shock absorber 306, a buffer plate 307, and a piezoelectric thin film sensor 308. Shock absorbers 306 are fixedly mounted on the second connecting members 303 at both ends, and a buffer plate 307 is fixedly connected between the two shock absorbers 306. A piezoelectric thin film sensor 308 is fixedly mounted on the upper surface of the buffer plate 307. The upper surface of the buffer plate 307 directly transmits force, and the piezoelectric thin film sensor 308 monitors the magnitude of the force. Simultaneously, the shock absorbers 306 at both ends of the buffer plate 307 provide vibration damping.

[0065] The second monitoring buffer head includes a shock absorber 306, a buffer plate 307, and a piezoelectric film sensor 308. The shock absorbers 306 are fixedly mounted on the second supporting hydraulic cylinders 305 at both ends, and the buffer plate 307 connects the two shock absorbers 306. The piezoelectric film sensor 308 is mounted on the lower end surface of the buffer plate 307. The lower end surface of the buffer plate 307 directly contacts and transmits force, and the piezoelectric film sensor 308 monitors the magnitude of the force. Simultaneously, the shock absorbers 306 at both ends of the buffer plate 307 provide vibration damping.

[0066] The shock absorber 306 can perform damping and vibration reduction, and its own damping magnitude can be adjusted. Specifically, it includes a support sleeve 3061, a load-bearing sleeve 3062, a damping rod 3063, an oil delivery pipe 3064, a piston 3065, a guide sleeve 3066, a buffer chamber 3067, an inlet solenoid valve 3068, an oil pump 3069, and a reversing valve 3070.

[0067] The support sleeve 3061 is provided with a telescopic shock absorber 3063. One end of the shock absorber 3063 extends out of the support sleeve 3061 to be fixedly connected with the buffer plate 307. The support sleeve 3061 and the bearing sleeve 3062 are fixedly provided with guide sleeves 3066. The other end of the shock absorber 3063 is sleeved in the guide sleeve 3066 to ensure the stable and reliable telescopic movement of the shock absorber 3063.

[0068] The shock absorber rod 3063 is equipped with a piston 3065 located inside the support sleeve 3061. The inside of the support sleeve 3061 is divided into an upper oil chamber and a lower oil chamber by the piston 3065. The upper oil chamber and the lower oil chamber are connected by an oil delivery pipe 3064 to realize the flow of oil between the upper and lower oil chambers to achieve the damping effect.

[0069] The support sleeve 3061 is fixedly sleeved on the bearing sleeve 3062, and the bearing sleeve 3062 supports the support sleeve 3061. The bearing sleeve 3062 is fixed to the connector or hydraulic cylinder. A buffer cavity 3067 communicating with the lower oil cavity is formed between the support sleeve 3061 and the bearing sleeve 3062, and the oil in the lower oil cavity can be temporarily stored through the buffer cavity 3067.

[0070] The support sleeve 3061 is a sealed cavity that houses the piston 3065 and the shock absorber rod 3063. It can be made of high-strength alloy steel, with its inner wall precision-machined to form a smooth contact surface, ensuring low-friction characteristics of the piston 3065's movement. The guide sleeve 3066 is a limiting structure that constrains the movement trajectory of the shock absorber rod 3063. It can be made of a copper-based self-lubricating bushing, with its inner hole clearance-fitted to the shock absorber rod 3063 to prevent seal failure caused by lateral sway. The oil delivery pipe 3064 is a channel connecting the upper and lower oil chambers of the piston 3065. It can be made of a high-pressure resistant hose or a built-in drilled flow channel, achieving pressure self-balancing through bidirectional oil flow.

[0071] When the guide vane vibrates or displaces during operation, the damping rod 3063, under load, pushes the piston 3065 to move within the support sleeve 3061, causing an imbalance in oil pressure on both sides of the piston 3065. Oil on the high-pressure side flows to the low-pressure side through the oil delivery pipe 3064, with some oil temporarily stored in the buffer chamber 3067 to dissipate energy. When the load direction changes, the oil flows in the opposite direction to replenish the low-pressure area, forming a dynamic pressure balance. The guide sleeve 3066 axially constrains the extension and retraction trajectory of the damping rod 3063, preventing seal wear caused by misalignment. The buffer chamber 3067, acting as an oil storage area, absorbs instantaneous pressure fluctuations. This structure achieves adaptive damping adjustment through autonomous oil flow, without relying on external control signals.

[0072] Traditional shock absorbers often employ a fixed damping coefficient design, which can easily lead to insufficient damping or overload lock-up under sudden changes in operating conditions. This solution establishes dynamic communication between the two sides of piston 3065 through the oil delivery pipe 3064, allowing the oil to autonomously distribute according to the pressure difference, forming a real-time responsive variable damping mechanism. Existing technologies often rely on solenoid valves for active control of the oil circuit; this solution eliminates the active control element, utilizing a mechanical structure to achieve passive adaptive adjustment, reducing system complexity and avoiding the reliability issues of electromagnetic components in humid environments.

[0073] This design automatically adjusts the damping characteristics of the guide vane under dynamic loads. When water flow impact intensifies guide vane vibration, rapid oil flow reduces system stiffness. When the load stabilizes, oil recirculation restores the basic damping value. This adaptive process effectively suppresses the continuous accumulation of guide vane opening deviation, prevents mechanical jamming caused by local overload, and maintains the synchronicity and stability of guide vane movement.

[0074] The support sleeve 3061 is equipped with an inlet solenoid valve 3068 that connects the buffer chamber 3067 and the lower oil chamber, for conveying oil between the buffer chamber 3067 and the lower oil chamber of the support sleeve 3061. The buffer chamber 3067 is connected to the oil pump 3069 through a pipeline, and the oil pump 3069 is connected to the reversing valve 3070 through a pipeline. The reversing valve 3070 is connected to the upper oil chamber and the lower oil chamber through pipelines respectively.

[0075] The inlet solenoid valve 3068 is an electromagnetic control valve that controls the flow of oil between the buffer chamber 3067 and the lower oil chamber of the support sleeve 3061. Specifically, it can be implemented using a two-position two-way solenoid valve. The oil exchange rate is adjusted by controlling the opening and closing of the valve. The oil pump 3069 is a power component used to pressurize and deliver the oil in the buffer chamber 3067 to the inside of the support sleeve 3061. Specifically, it can be implemented using a gear pump or a piston pump. The damping parameters are adjusted by changing the oil delivery direction and flow rate. The directional valve 3070 is a hydraulic control valve that controls the direction of oil flow. Specifically, it can be implemented using a three-position four-way solenoid directional valve. The oil is directed to the upper or lower oil chamber of the piston by switching the oil circuit.

[0076] When the internal oil pressure of the support sleeve 3061 needs adjustment due to changes in external load, the inlet solenoid valve 3068 opens according to a control signal, allowing oil to flow between the buffer chamber 3067 and the support sleeve 3061. The oil pump 3069 pressurizes the oil stored in the buffer chamber 3067 and delivers it to the reversing valve 3070, which switches the oil circuit direction according to a pressure sensor signal. When the upper region of the piston 3065 requires increased damping, the reversing valve 3070 directs oil to that region to increase local oil pressure. When the lower region of the piston 3065 requires pressure compensation, the reversing valve 3070 switches to the reverse oil circuit, and oil is delivered to the lower region. This closed-loop control of the oil circulation path allows the internal oil pressure distribution of the support sleeve 3061 to match the dynamic changes in external load in real time, forming an adaptive damping adjustment mechanism.

[0077] Traditional dampers use fixed orifices or manual regulating valves to control oil flow, which cannot respond to load changes in real time. This solution constructs a closed-loop system that can dynamically adjust the oil flow direction and flow rate through the coordinated control of solenoid valves and oil pumps. While maintaining the fast response of passive damping, it adds active adjustment capability based on real-time pressure feedback, solving the problem of buffer failure caused by damping parameter mismatch under sudden loads.

[0078] This application achieves dynamic adjustment of the buffer damping parameters, enabling the internal oil pressure distribution of the support sleeve 3061 to automatically match changes in external load, thus solving the problem of insufficient energy absorption efficiency caused by fixed damping parameters in traditional shock absorbers 306. The closed-loop control mechanism of the oil circulation system can compensate for the oil pressure difference between the upper and lower regions of the piston 3065 in real time, avoiding structural vibration caused by local pressure imbalance and improving the operational stability of the buffer adjustment component 3 over a wide range of operating conditions.

[0079] The support sleeve 3061 and the bearing sleeve 3062 are separated into a buffer cavity 3067 and an inter-sleeve cavity by a partition. The oil pump 3069 is located in the inter-sleeve cavity. That is, the inter-sleeve cavity of the bearing sleeve 3062 provides installation space for adjustment components such as the oil pump 3069. The inter-sleeve cavity of the bearing sleeve 3062 and the buffer cavity 3067 are functionally partitioned by an internal partition. Specifically, the partition structure can be formed by welding or casting. The cavity is used to accommodate auxiliary components such as the oil pump 3069, and the buffer cavity 3067 serves as a temporary oil storage space.

[0080] The buffer plate 307 refers to the rigid load-bearing structure installed on the end face. It can be made of high-strength alloy steel plate, with its flatness error controlled at the micrometer level. The surface is polished to reduce friction loss. Serving as a pressure transmission interface, it uniformly distributes the mechanical load to the piezoelectric thin-film sensor 308. The piezoelectric thin-film sensor 308 is a flexible thin-film pressure-sensitive element made of polyvinylidene fluoride (PVDF). It can employ a multi-layered structure and form an electrode layer on its surface through a sputtering process. It can convert mechanical stress perpendicular to the film surface into an electrical charge signal output, exhibiting wide frequency response and high linearity, achieving millisecond-level response under dynamic loads.

[0081] The buffer plate 307 is directly coupled to the mechanical contact surface of the guide vane transmission mechanism. When dynamic deviations occur during guide vane opening adjustment, the axial pressure or lateral shear force transmitted by the guide vane control linkage is stress-dispersed through the buffer plate 307. The piezoelectric thin film sensor 308 quantifies the magnitude and direction of the load-bearing pressure in real time through charge change. The charge signal is converted into a voltage signal by a charge amplifier and then input to the control system, forming a real-time monitoring of the guide vane's operating status. The high rigidity of the buffer plate 307 ensures no hysteresis deformation in the pressure transmission path, and the flexible bonding characteristics of the piezoelectric thin film avoid stress concentration between the sensor and the rigid structure. At the same time, the multi-layer electrode design suppresses electromagnetic interference from disturbing the weak charge signal, enabling the pressure monitoring data to accurately reflect the actual stress state of the guide vane and providing precise input for subsequent adaptive correction.

[0082] Traditional guide vane opening monitoring systems rely solely on encoders or displacement sensors to acquire angle signals, failing to directly detect changes in mechanical load within the guide vane drivetrain. This results in a lag in identifying abnormal conditions such as jamming and asynchrony. In contrast, this solution integrates a piezoelectric thin-film sensor on the component end face, establishing a direct conversion channel between mechanical and electrical signals. This not only captures pressure fluctuations during guide vane movement in real time but also identifies potential faults such as guide vane journal jamming and connecting rod deformation through pressure distribution characteristics, overcoming the technical deficiency of traditional monitoring methods' insensitivity to changes in mechanical load.

[0083] This solution enables real-time sensing and precise quantification of the pressure carried during the dynamic adjustment of the guide vane opening. By embedding the pressure monitoring function into the mechanical structure of the buffer adjustment component, it avoids the signal attenuation and interference problems caused by the installation of external sensors, providing a high-precision data foundation for the identification of abnormal guide vane status and adaptive correction control, and effectively improving the monitoring sensitivity and adjustment reliability of the hydropower unit guide vane system.

[0084] The guide vane end cover 4 is provided with a shaft hole 401, a toothed hole 402, and a guide vane end cover bolt hole 403. After passing through the shaft hole 401, the toothed hole 402 is aligned with the shaft bolt hole 202, and the guide vane end cover bolt hole 403 is aligned with the guide vane cover bolt hole 106, and is fixed by bolts.

[0085] The shaft hole 401 is a through hole that penetrates the center of the guide vane end cover 4 and matches the outer diameter of the shaft. It can be precision machined to form a stepped hole structure to constrain the axial displacement of the shaft and ensure its concentricity with the guide vane 1. The bevel gear hole 402 is a positioning hole distributed circumferentially around the guide vane end cover 4 and matching the contour of the bevel gear 203. It can be implemented using a pentagonal countersunk hole structure to define the relative circumferential position of the bevel gear 203 and the shaft. The guide vane end cover bolt hole 403 is a threaded hole evenly distributed along the edge of the guide vane end cover 4. It can be implemented using an indexing plate positioning drilling process to form a one-to-one correspondence with the guide vane cover bolt holes 106 of the guide vane 1 to achieve multi-point rigid connection.

[0086] After the shaft passes through the shaft hole 401 for axial positioning, the correspondence between the bevel gear hole 402 and the shaft bolt hole 202 is constrained in the circumferential degree of freedom by the geometric shape of the bevel gear 203, eliminating transmission errors caused by rotational deviations during assembly. The guide vane end cover bolt hole 403 and the guide vane end cover bolt hole 106 form a bolt group connection after indexing and positioning. Preload is used to press the guide vane end cover 4 tightly onto the surface of the guide vane 1 body, preventing loosening of the connection caused by water impact or vibration. During installation, the shaft hole 401, bevel gear hole 402, and guide vane end cover bolt hole 403 sequentially form three levels of constraints: axial, circumferential, and overall fixation, eliminating accumulated errors through step-by-step assembly.

[0087] Traditional guide vane end caps use only a single bolt hole for fixing, which cannot constrain the circumferential relative position of the shaft and guide vane 1, and the lack of a multi-stage positioning structure means that installation accuracy depends on manual adjustment. This solution achieves automatic alignment of the shaft and guide vane 1 through the coordinated positioning of the shaft hole 401 and the angular tooth hole 402. At the same time, the distribution of multiple bolt holes forms surface contact and clamping, significantly improving the connection rigidity.

[0088] This application solves the positioning deviation problem when the guide vane end cover 4 is connected to the shaft mechanism 2 and the guide vane 1. It achieves self-alignment of assembly through a three-level constraint structure, avoids dynamic deviation of the guide vane 1 opening caused by misalignment, and enhances the vibration resistance of the connection structure to ensure the long-term stability of the guide vane 1 transmission system.

[0089] Example 2 refer to Figures 1-9 As shown, a dynamic deviation monitoring and adaptive correction system for the guide vane opening of a hydroelectric generator includes a piston cylinder 5, a control ring 6, a guide vane control linkage 7, and a guide vane control hydraulic cylinder 8. It also includes the dynamic deviation monitoring and adaptive correction device for the guide vane opening of the hydroelectric generator as described in Embodiment 1.

[0090] The guide vane control linkage 7 is connected to the shaft mechanism 2, the guide vane control linkage 7 is connected to the guide vane control hydraulic cylinder 8, several guide vane control hydraulic cylinders 8 are all connected to the control ring 6, and the control ring 6 is connected to the piston cylinder 5.

[0091] The shaft 201 refers to the rotating shaft component rigidly connected to the transmission mechanism of the guide vane 1. Specifically, it can be made of high-strength alloy steel, machined into a stepped shaft structure, and nitrided to improve wear resistance. Its function is to convert the angular displacement of the guide vane 1 into mechanical torque output. The guide vane control linkage 7 refers to the rigid transmission rod connecting the shaft 201 and the hydraulic actuator. Specifically, it can adopt a combination structure of ball joint and universal joint to achieve multi-degree-of-freedom motion transmission. Its function is to eliminate the influence of installation errors on transmission accuracy. The guide vane control hydraulic cylinder 8 refers to a linear actuator using hydraulic oil as the power medium. Specifically, it can adopt a double-rod symmetrical cylinder structure and integrate a high-precision displacement sensor. Its function is to convert electro-hydraulic servo signals into precise push-pull force output. The control ring 6 refers to the annular linkage mechanism arranged around the guide vane 1 group. Specifically, it can adopt a split cast steel ring body connected by flange bolts. Its function is to synchronously drive multiple guide vane control hydraulic cylinders 8 to achieve group control coordination. The piston cylinder 5 provides the power for the movement of the control ring 6.

[0092] The shaft section 201 and the guide vane control linkage 7 are connected by a spline to transmit torque. When the guide vane 1 rotates, it drives the linkage to produce linear displacement. The piston rod end of the guide vane control hydraulic cylinder 8 is hinged to the linkage, and the cylinder body is fixed to the unit's foundation frame by a trunnion. When the hydraulic system supplies oil to the cylinder, the piston rod pushes the linkage to move, which in turn drives the shaft section 201 to rotate to adjust the opening of the guide vane 1. The control ring 6 is connected to the cylinder body of each guide vane control hydraulic cylinder 8 through a rigid connector. When the central controller issues an adjustment command, the hydraulic system synchronously supplies oil to all cylinders, causing the control ring 6 to drive each cylinder to move synchronously. During this process, the displacement sensor built into the hydraulic cylinder provides real-time feedback on the piston position, forming a closed-loop control circuit.

[0093] Traditional guide vane 1 adjustment systems rely on purely mechanical linkage transmission, which suffers from cumulative transmission backlash errors and inertial hysteresis. This solution, however, eliminates the effects of elastic deformation in mechanical transmission by combining hydraulic drive with closed-loop control. Existing independent adjustment methods for single guide vanes are prone to asynchrony between groups; this solution achieves coordinated action of multiple guide vanes 1 through a rigid synchronization mechanism in control loop 6. Current technologies lack real-time feedback compensation mechanisms; this solution achieves dynamic error correction through the coordinated adjustment of sensors and servo valves.

[0094] This solution resolves the uneven flow distribution caused by asynchronous movement of the guide vanes (Group 1), reduces the impact of hydraulic system response delay on adjustment accuracy, and eliminates the accumulation of opening deviations caused by mechanical transmission backlash. The high-pressure drive characteristics of the guide vane control hydraulic cylinder 8 overcome the fluctuations in adjustment torque caused by hydraulic pulsation, and the rigid synchronization structure of the control loop 6 ensures millisecond-level consistency in the opening of multiple guide vanes (Group 1). Real-time feedback from the displacement sensor enables the guide vane (Group 1) opening adjustment accuracy to reach the micrometer level, meeting the rapid response requirements under transient turbine conditions.

[0095] The foregoing basic examples and their further alternative examples can be freely combined to form multiple embodiments, all of which are embodiments that can be adopted and claimed in this application. In the scheme of this application, each alternative example can be arbitrarily combined with any other basic example and alternative example.

[0096] The above description is merely a preferred embodiment of this application and is not intended to limit this application. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of this application should be included within the protection scope of this application.

Claims

1. A kind of water turbine guide vane opening dynamic deviation monitoring and adaptive correction device, including guide vane (1) and shaft mechanism (2), it is characterized in that: The guide vane (1) is provided with a star-shaped tooth groove (102), the shaft rod mechanism (2) is provided with a star-shaped angular tooth (203) matched with the tooth groove (102), the angular tooth (203) is located in the tooth groove (102) and a plurality of gaps are formed between the two, a plurality of buffer adjusting components (3) located in the gaps are arranged between the guide vane (1) and the shaft rod mechanism (2), and the end of the guide vane (1) and the end of the shaft rod mechanism (2) are connected with a guide vane end cover (4).

2. The dynamic bias monitoring and self-adaptive correction device for guide vane opening degree of a hydroelectric generating unit according to claim 1, characterized in that: The tooth groove (102) and the angular tooth (203) are mutually matched five-pointed stars.

3. The dynamic deviation monitoring and self-adaptive correction device for guide vane opening degree of a hydroelectric generating unit according to claim 1 or 2, characterized in that: The guide vane (1) comprises two guide vane parts (101), the guide vane part (101) is provided with a part tooth groove, the part tooth grooves on the two guide vane parts (101) are jointly connected to form the tooth groove (102), and the side surface of the guide vane part (101) is provided with an anti-scratching film (103).

4. The dynamic bias monitoring and self-adaptive correction device for guide vane opening degree of a hydroelectric generating unit according to claim 3, characterized in that: The two side edges of the guide vane part (101) are provided with insertion grooves (104), the insertion grooves (104) on the same side edge are provided with an insertion seat (105), the two ends of the insertion seat (105) are respectively inserted into the insertion grooves (104) of the two guide vane parts (101), and the insertion seat (105) is connected with the guide vane part (101) through bolts.

5. The dynamic deviation monitoring and self-adaptive correction device for guide vane opening degree of a hydroelectric generating unit according to claim 1 or 2, characterized in that: The shaft rod mechanism (2) comprises a shaft rod part (201), and the shaft rod part (201) is provided with the angular tooth (203).

6. The hydraulic power unit guide vane opening dynamic deviation monitoring and self-adaptive correction device according to claim 1, characterized in that: The buffer adjusting component (3) comprises a first connecting piece (301), the two ends of the first connecting piece (301) are respectively connected with dampers (302), the two dampers (302) are respectively hingedly connected with a second connecting piece (303), the lower parts of the two second connecting pieces (303) are respectively connected with the upper parts of second supporting hydraulic cylinders (305), the two second supporting hydraulic cylinders (305) are respectively hingedly connected with first supporting hydraulic cylinders (304) between the two ends of the lower part of the first connecting piece (301), the upper parts of the two second connecting pieces (303) are jointly provided with first monitoring buffer heads in contact with the guide vane (1), and the lower parts of the two second supporting hydraulic cylinders (305) are jointly provided with second monitoring buffer heads in contact with the shaft rod mechanism (2).

7. The dynamic bias monitoring and self-adaptive correction device for guide vane opening of a hydroelectric generating unit according to claim 6, characterized in that: The first monitoring buffer head comprises a shock absorber (306), a buffer plate (307) and a piezoelectric film sensor (308), the two second connecting pieces (303) are respectively provided with the shock absorbers (306), the two shock absorbers (306) are connected with the buffer plate (307), and the upper end surface of the buffer plate (307) is provided with the piezoelectric film sensor (308); the second monitoring buffer head comprises a shock absorber (306), a buffer plate (307) and a piezoelectric film sensor (308), the two second supporting hydraulic cylinders (305) are respectively provided with the shock absorbers (306), the two shock absorbers (306) are connected with the buffer plate (307), and the lower end surface of the buffer plate (307) is provided with the piezoelectric film sensor (308).

8. The dynamic bias monitoring and self-adaptive correction device for guide vane opening degree of a hydroelectric generating unit according to claim 7, characterized in that: The damper (306) comprises a supporting sleeve (3061) provided with an elastic shock rod (3063) capable of stretching and retracting, and a piston (3065) provided on the elastic shock rod (3063) and located in the supporting sleeve (3061); the inside of the supporting sleeve (3061) is divided into an upper oil chamber and a lower oil chamber by the piston (3065), the upper oil chamber and the lower oil chamber are communicated through an oil delivery pipe (3064), the supporting sleeve (3061) is sleeved on a bearing sleeve (3062), and the supporting sleeve (3061) and the bearing sleeve (3062) form a buffer chamber (3067) communicated with the lower oil chamber.

9. The dynamic bias monitoring and self-adaptive correction device for guide vane opening degree of a hydroelectric generating unit according to claim 8, characterized in that: The supporting sleeve (3061) is provided with a liquid inlet electromagnetic valve (3068) communicated with the buffer chamber (3067) and the lower oil chamber, the buffer chamber (3067) is communicated with an oil pump (3069) through a pipeline, the oil pump (3069) is communicated with a reversing valve (3070) through a pipeline, and the reversing valve (3070) is communicated with the upper oil chamber and the lower oil chamber through pipelines.

10. A dynamic deviation monitoring and adaptive correction system for guide vane opening of a hydroelectric generating unit, comprising a guide vane control link (7), characterized in that, The hydraulic turbine guide vane opening dynamic deviation monitoring and self-adaptive correction device comprises a guide vane control connecting rod (7) connected with the shaft rod mechanism (2), a guide vane control hydraulic cylinder (8) connected with the guide vane control connecting rod (7), and a plurality of guide vane control hydraulic cylinders (8) connected with the control ring (6), and the control ring (6) is connected with the piston cylinder (5).

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