Double-cylinder driving rack type guide vane adjusting mechanism and adjusting method thereof

Abstract

The invention relates to a double-cylinder driving rack type guide vane adjusting mechanism and an adjusting method thereof.The adjusting mechanism comprises guide vanes, a synchronous adjusting disc and a hydraulic driving component, the guide vanes comprise shifting forks, guide vane shafts and vanes, the vanes are fixed to the guide vane shafts, the multiple guide vane shafts are evenly arranged on a shell, a circle of pin shafts are arranged on the synchronous adjusting disc, and the hydraulic driving component is arranged on the synchronous adjusting disc; one end of the shifting fork is fixed with the guide vane shaft, the other end of the shifting fork is sleeved on the pin shaft, a gear is further arranged on the synchronous adjusting disc, the hydraulic driving component comprises a rack, a hydraulic cylinder A and a hydraulic cylinder B, the rack is meshed with the gear, and the hydraulic control assembly comprises an oil tank, a motor, a hydraulic pump and a servo valve. The extension of the hydraulic cylinder A and the retraction of the hydraulic cylinder B synchronously act by controlling the servo valve, so that the rack moves to drive the synchronous adjusting disc to rotate, and the angle adjustment of the guide vane is realized. The adjusting mechanism is reliable in structural design, high in precision and high in response speed, it can be guaranteed that the power generation frequency of the wind turbine generator is constant, and high-quality electric energy is directly generated.

Description

Technical Field

[0001] This invention relates to the field of guide vane adjustment structure technology for hydraulic torque converters, specifically to a dual-cylinder driven rack and pinion guide vane adjustment mechanism and its adjustment method. Background Technology

[0002] Due to the increasing severity of energy shortages and environmental problems, the development and utilization of renewable energy has received widespread attention from countries around the world. With the rapid development of renewable energy technologies, wind power generation technology is becoming increasingly mature, and the total number of wind turbine units installed is constantly increasing. Traditional variable-speed constant-frequency wind turbine units require frequency converters for grid connection, which suffers from high gearbox failure rates and complex frequency conversion technology. As the capacity of individual units continues to increase, reliability decreases, and the mean time between failures (MTBF) increases; furthermore, the increased number of failures leads to rising installation and maintenance costs. The manufacturing, installation, operation, and maintenance of traditional variable-speed constant-frequency wind turbine units have reached a bottleneck.

[0003] To avoid the adverse effects of frequency converters on variable speed constant frequency wind turbines, meet increasingly stringent grid connection requirements for wind turbines, improve the reliability of wind turbines, and extend their service life, variable speed constant frequency wind turbines based on hydraulic speed regulation technology have emerged. The hydraulic torque converter of the wind turbine achieves constant speed operation of the synchronous generator by adjusting the adjustable guide vane blades, ensuring a constant power generation frequency and directly generating high-quality electrical energy. Summary of the Invention

[0004] To solve the above-mentioned technical problems, the first objective of this invention is to provide a guide vane adjustment mechanism with reliable structural design, high precision, and fast response speed. The second objective of this invention is to provide a dual-cylinder driven rack and pinion guide vane adjustment method.

[0005] To achieve the first objective of the invention, the present invention adopts the following technical solution:

[0006] A dual-cylinder driven rack and pinion guide vane adjustment mechanism includes an adjustment mechanism and a hydraulic control component. The adjustment mechanism includes guide vanes, a synchronous adjustment disc, and a hydraulic drive component. The guide vane includes a fork, a guide vane shaft, and blades. The blades are fixed on the guide vane shaft. Multiple guide vane shafts are evenly arranged circumferentially on a housing and are rotatably mounted on the housing. The synchronous adjustment disc is rotatably mounted on the housing and has a ring of pins. One end of the fork is fixed to the guide vane shaft, and the other end of the fork has an elongated through hole that fits onto the pins. The synchronous adjustment disc also has gears. The hydraulic drive component includes a rack and hydraulic cylinders A and B connected to both ends of the rack. The rack meshes with the gears.

[0007] The hydraulic control component includes an oil tank, a motor, a hydraulic pump, and a servo valve. The motor drives the hydraulic pump to input oil from the oil tank into the servo valve. The output port of the servo valve is connected to hydraulic cylinder A and hydraulic cylinder B respectively. By controlling the servo valve, the extension of hydraulic cylinder A and the retraction of hydraulic cylinder B are synchronized, or the retraction of hydraulic cylinder A and the extension of hydraulic cylinder B are synchronized. This causes the rack to move and drive the synchronous adjustment disc to rotate, thereby realizing the angle adjustment of the guide vane.

[0008] As a preferred embodiment, the synchronization adjustment disc includes a disc and a boss, the pin is disposed on the outer edge of one side of the disc, the boss is disposed on the inner edge of one side of the disc, and the gear is disposed on the boss.

[0009] As a preferred embodiment, the hydraulic rod A of the hydraulic cylinder A is fixedly connected to one end of the rack, and the other end of the rack is fixedly connected to the hydraulic rod B of the hydraulic cylinder B.

[0010] As a preferred embodiment, a check valve and a filter device are connected in sequence between the servo valve and the hydraulic pump, and the filter device integrates an alarm device.

[0011] As a preferred embodiment, a bypass oil circuit is provided between the filter device and the servo valve, which is connected to the accumulator. The bypass oil circuit is also provided with a switching valve and a shut-off valve, and a pressure and flow sensor is provided between the switching valve and the shut-off valve.

[0012] As a preferred embodiment, the hydraulic pump and the servo valve are further provided with a return oil pipeline connected to the oil tank, and the return oil pipeline is provided with a switching valve, an overflow valve and a cooling device.

[0013] As a preferred embodiment, the cooling device includes a cooling motor, a fan, and a cooler. The oil in the return oil pipeline flows back to the oil tank through the cooler, and the cooling motor drives the fan to rotate and dissipate the heat of the oil inside the cooler.

[0014] As a preferred embodiment, both hydraulic cylinder A and hydraulic cylinder B have built-in displacement sensors. Hydraulic cylinder A is also equipped with a limit switch A, and hydraulic cylinder B is also equipped with a limit switch B. The servo valve controls the position of hydraulic rod A of hydraulic cylinder A and hydraulic rod B of hydraulic cylinder B based on the signals from the displacement sensor, limit switch A, and limit switch B.

[0015] As a preferred embodiment, the oil tank is also equipped with auxiliary components, including a thermometer for monitoring the temperature of the oil inside the tank, a filter for monitoring the cleanliness of the oil inside the tank, and a level gauge for monitoring the oil level inside the tank.

[0016] To achieve the second objective of the invention, the present invention adopts the following technical solution:

[0017] A method for adjusting a dual-cylinder driven rack and pinion guide vane, employing any one of the aforementioned dual-cylinder driven rack and pinion guide vane adjusting mechanisms, includes the following steps:

[0018] (1) When the control signal for reducing the guide vane opening is received, the motor drives the hydraulic pump to rotate and pump out oil. The servo valve in the left position works T1. Part of the oil flows into the rod chamber of hydraulic cylinder A, and the other part flows into the rodless chamber of hydraulic cylinder B. The synchronous action of hydraulic cylinder A retracting and hydraulic cylinder B extending is controlled respectively. The rack meshing with the gear drives the gear to rotate counterclockwise. The blade rotates counterclockwise around the guide vane shaft, and the guide vane opening decreases.

[0019] (2) When the control signal for increasing the guide vane opening is received, the motor drives the hydraulic pump to rotate and pump out oil. The right position function T2 of the servo valve is working. Part of the oil flows into the rodless chamber of hydraulic cylinder A, and the other part flows into the rodless chamber of hydraulic cylinder B. The synchronous action of hydraulic cylinder A extending and hydraulic cylinder B retracting is controlled respectively. The rack meshing with the gear drives the gear to rotate clockwise. The blade rotates clockwise around the guide vane shaft, and the guide vane opening increases.

[0020] This invention focuses on the technical requirements of the hydraulic torque converter in the front-end speed control system of wind turbine generators. Addressing the technical challenges of severe dynamic load fluctuations, continuous high-torque operation, and stringent power quality requirements in wind turbine generators, this invention proposes a guide vane adjustment mechanism that combines a hydraulic drive system with a gear and rack mechanism. This achieves multiple technical breakthroughs in terms of structural reliability, adjustment precision, drive adaptability, and power output quality. Specific beneficial effects are as follows:

[0021] 1. Structural Design Dimension: Dual Improvement in Reliability and Maintainability

[0022] Traditional guide vane adjustment mechanisms often employ ball screw connections. Under the long-term, high-torque, high-frequency adjustment conditions of wind turbines, this type of structure is prone to problems such as screw wear and increased transmission backlash, which not only reduces adjustment accuracy but also significantly increases equipment maintenance costs and downtime risks. This invention employs a gear and rack rotation mechanism for the guide vane, whose transmission pair has the advantages of stable meshing characteristics, uniform wear, and easy detection. From a mechanical structure perspective, the line contact transmission of the gear and rack effectively distributes the load and maintains transmission stiffness under high torque conditions, avoiding premature failure of the ball screw due to localized stress concentration. Simultaneously, this structure eliminates the complex lubrication and sealing system of the ball screw, significantly reducing the mechanical complexity of the mechanism. Routine maintenance only requires monitoring the meshing state and wear degree of the gear and rack, simplifying the maintenance process and reducing costs. This greatly improves the reliability and maintainability of the guide vane adjustment mechanism throughout the entire life cycle of the wind turbine, providing a solid structural guarantee for the continuous and stable operation of the wind turbine.

[0023] 2. Adjusting performance dimensions: synergistic optimization of accuracy and synchronization

[0024] The gear and rack mechanism of this invention possesses inherent linear transmission characteristics, with a constant transmission ratio unaffected by stroke. Combined with the high-precision characteristics of the synchronous adjustment disc, it ensures a high degree of angular consistency among multiple guide vanes during adjustment. From a kinematic perspective, the transmission linearity of the gear and rack is far superior to common mating methods such as traditional ball screws. This high-precision synchronous adjustment characteristic makes the speed regulation process of the hydraulic torque converter smoother, avoiding internal flow field turbulence caused by asynchronous guide vane adjustment, thereby reducing energy loss and improving torque conversion efficiency. During wind fluctuations, this mechanism can quickly and accurately adjust the guide vane angle, ensuring the hydraulic torque converter always operates within its optimal operating range, laying a performance foundation for stable subsequent electrical energy output.

[0025] 3. Drive system dimension: Advantages in power characteristics and response speed become prominent

[0026] Compared to the electric drive systems commonly used for wind turbine speed regulation, the hydraulic drive system employed in this invention demonstrates significant advantages under the high torque and fast response requirements of wind turbines. From a power transmission principle perspective, the power density (output power per unit volume) of a hydraulic system is far higher than that of an electric drive system, providing the driving force required for high torque regulation within a compact structural space. The hydraulic system achieves precise adjustment through servo valve group control, enabling it to quickly capture instantaneous changes in wind conditions and promptly adjust the guide vane angle, ensuring that the wind turbine's power transmission system is always dynamically matched to the wind conditions. Furthermore, the dual hydraulic cylinders, one pulling and one extending, drive the guide vane adjustment. Compared to a single hydraulic cylinder, this provides a more balanced and responsive driving force, improving the efficiency of switching operating conditions. In terms of adjustment precision, it can offset the eccentric torque of unilateral force, making the guide vane movement smoother and the positioning more accurate. In terms of system reliability, it forms a redundant drive, so that if one hydraulic cylinder fails, the other cylinder can still maintain some functions, reducing the risk of downtime. In terms of structural stress, it makes the force on key components such as the guide vane shaft more even, reducing stress concentration and extending service life. Overall, it has significant advantages in terms of power performance, adjustment precision, reliability, and structural durability. Attached Figure Description

[0027] The accompanying drawings, which form part of this application, are used to provide a further understanding of this application. The illustrative embodiments of this application and their descriptions are used to explain this application and do not constitute a limitation thereof.

[0028] Figure 1 This is an overall assembly drawing of the guide vane adjustment mechanism of the present invention;

[0029] Figure 2 This is an exploded view of the guide vane adjustment mechanism of the present invention;

[0030] Figure 3 This is a schematic diagram of the layout structure of all guide vanes in this invention;

[0031] Figure 4 This is a schematic diagram of the structure of a single guide vane of the present invention;

[0032] Figure 5 This is a schematic diagram of the synchronous adjustment disk of the present invention;

[0033] Figure 6 This is a schematic diagram of the structure of the hydraulic drive component of the present invention;

[0034] Figure 7 This is a schematic diagram of the guide vane adjustment mechanism of the present invention in the fully closed state.

[0035] Figure 8 This is a schematic diagram of the guide vane adjustment mechanism of the present invention in the fully open state.

[0036] Figure 9 This is a hydraulic schematic diagram of the guide vane adjustment mechanism of the present invention.

[0037] The labels in the attached diagram are as follows: 1. Guide vane; 11. Shift fork; 12. Guide vane shaft; 13. Blade; 2. Synchronous adjustment disc; 21. Disc; 22. Pin; 23. Boss; 24. Gear; 3. Hydraulic drive component; 31. Hydraulic cylinder A; 32. Hydraulic rod A; 33. Rack; 34. Hydraulic rod B; 35. Hydraulic cylinder B; 401. Oil tank; 402. Motor; 403. Hydraulic pump; 404. Cooling device; 406. Check valve; 407. Filter device; 408. Switch valve; 409. Relief valve; 410. Switch valve; 411. Pressure and flow sensor; 412. Shut-off valve; 413. Accumulator; 414. Servo valve; 417. Displacement sensor; 418. Limit switch A; 419. Limit switch B. Detailed Implementation

[0038] It should be noted that the following detailed descriptions are illustrative and intended to provide further explanation of this application. Unless otherwise specified, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this application pertains.

[0039] It should be noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to limit the exemplary embodiments according to this application. As used herein, the singular form is intended to include the plural form as well, unless the context clearly indicates otherwise. Furthermore, it should be understood that when the terms "comprising" and / or "including" are used in this specification, they indicate the presence of features, steps, operations, devices, components, and / or combinations thereof.

[0040] Furthermore, in the description of this invention, it should be understood that the terms "center," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "clockwise," and "counterclockwise," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this invention.

[0041] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of indicated technical features. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of this invention, unless otherwise stated, "a plurality of" means two or more, unless explicitly defined otherwise.

[0042] In this invention, unless otherwise explicitly specified and limited, the terms "installation," "connection," "linking," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal connection of two components. Those skilled in the art can understand the specific meaning of the above terms in this invention according to the specific circumstances.

[0043] In this invention, unless otherwise explicitly specified and limited, "above" or "below" the second feature can include direct contact between the first and second features, or contact between the first and second features through another feature between them. Furthermore, "above," "over," and "on top" of the second feature includes the first feature directly above or diagonally above the second feature, or simply indicates that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature includes the first feature directly below or diagonally below the second feature, or simply indicates that the first feature is at a lower horizontal level than the second feature.

[0044] The present invention will be further described below with reference to the accompanying drawings and embodiments:

[0045] like Figures 1 to 9As shown, a dual-cylinder driven rack and pinion guide vane adjustment mechanism includes an adjustment mechanism and a hydraulic control component. The adjustment mechanism includes a guide vane 1, a synchronous adjustment disc 2, and a hydraulic drive component 3. The guide vane 1 includes a fork 11, a guide vane shaft 12, and blades 13. The blades 13 are fixed on the guide vane shaft 12. Multiple guide vane shafts 12 are evenly arranged circumferentially on the housing and are rotatably mounted to the housing. The synchronous adjustment disc 2 is rotatably mounted to the housing and has a ring of pins 22. One end of the fork 11 is fixed to the guide vane shaft 12, and the other end of the fork 11 has an elongated through hole that fits onto the pins 22. The synchronous adjustment disc 2 also has a gear 24. The hydraulic drive component 3... The system includes a rack 33 and hydraulic cylinders A31 and B35 connected to both ends of the rack 33. The rack 33 meshes with a gear 24. The hydraulic control assembly includes an oil tank 401, a motor 402, a hydraulic pump 403, and a servo valve 414. The motor 402 drives the hydraulic pump 403 to input oil from the oil tank 401 to the servo valve 414. The output port of the servo valve 414 is connected to hydraulic cylinders A31 and B35 respectively. By controlling the servo valve 414, the extension of hydraulic cylinder A31 and the retraction of hydraulic cylinder B35 are synchronized, or the retraction of hydraulic cylinder A31 and the extension of hydraulic cylinder B35 are synchronized. This causes the rack 33 to move, driving the synchronous adjustment disc 2 to rotate, thereby achieving the angle adjustment of the guide vane 1.

[0046] The servo valve 414 controls the flow of oil into the chambers of hydraulic cylinders A31 and B35, and controls the direction of movement of hydraulic cylinders A31 and B35. Furthermore, the servo valve 414 can also control the oil flow rate, thereby controlling the movement speed of hydraulic cylinders A31 and B35. Both hydraulic cylinders A31 and B35 have built-in displacement sensors 417. Hydraulic cylinder A31 also has a limit switch A418 externally, and hydraulic cylinder B35 has a limit switch B419 externally. Based on the signals from the displacement sensors 417, limit switches A418, and B419, the servo valve 414 controls the position of the hydraulic rod A32 of hydraulic cylinder A31 and the hydraulic rod B34 of hydraulic cylinder B35, thereby controlling the change in guide vane opening.

[0047] The synchronous adjustment disc 2 includes a disc 21 and a boss 23. The pin 21 is located on the outer edge of one side of the disc 21, and the boss 23 is located on the inner edge of one side of the disc 21. The gear 24 is mounted on the boss 23. The hydraulic rod A32 of the hydraulic cylinder A31 is fixedly connected to one end of the rack 33, and the other end of the rack 33 is fixedly connected to the hydraulic rod B34 of the hydraulic cylinder B35.

[0048] The hydraulic cylinders A31 and B35 are horizontally symmetrically connected. The hydraulic rods A32 and B34 retract and extend respectively, driving the rack 33 to move horizontally. Due to the meshing relationship, the gear 24 of the synchronous adjustment disc 2 converts the horizontal movement of the rack 33 into the rotational movement of the gear 24. The boss 23 synchronously transmits the rotational movement of the gear 24 to the disc 21. The pin 22 of the synchronous adjustment disc 2 is connected to the fork 11 of the guide vane 1. The rotational movement of the disc 21 drives the blade 13 in the guide vane 1 to rotate around the guide vane shaft 12, corresponding to different guide vane opening changes.

[0049] A one-way valve 406 and a filter device 407 are sequentially connected between the servo valve 414 and the hydraulic pump 403, and the filter device 407 integrates an alarm device. A bypass oil circuit connecting the filter device 407 and the servo valve 414 to the accumulator 413 is also provided. The bypass oil circuit is equipped with a switching valve 410 and a shut-off valve 412, and a pressure and flow sensor 411 is located between the switching valve 410 and the shut-off valve 412. The accumulator 413 can replenish oil to hydraulic cylinders A31 and B35 in a timely manner, improving the system response speed and preventing cavitation. The switching valve 410 and the shut-off valve 412 control the on / off state of the accumulator.

[0050] A return oil pipeline connected to the oil tank 401 is also provided between the hydraulic pump 403 and the servo valve 414. The return oil pipeline is equipped with a switch valve 408, a relief valve 409, and a cooling device 404. The cooling device 404 includes a cooling motor, a fan, and a cooler. The oil in the return oil pipeline flows back to the oil tank 401 through the cooler. The cooling motor drives the fan to rotate and dissipate the heat of the oil inside the cooler.

[0051] The one-way valve 406 controls the oil flow direction and prevents backflow. The filter device 407 ensures the cleanliness of the oil at the inlet of the servo valve 414 through its filtering function. The filter device 407 integrates an alarm device to achieve real-time monitoring of oil cleanliness. The switching valve 408 and the relief valve 409 function as safety valves. The relief valve sets the system safety pressure. When the oil exceeds the safety pressure, it is unloaded and returned to the oil tank through the relief valve 409. The switching valve 408 can unload the oil by controlling the electromagnet. The auxiliary components include a thermometer, a filter, and a level gauge, which are responsible for monitoring the oil temperature, cleanliness, and liquid level inside the oil tank.

[0052] The working functions of the guide vane adjustment mechanism of the present invention are as follows: The hydraulic drive component 3 is responsible for providing power to the guide vane adjustment mechanism, serving as the active component of the mechanism. The synchronous adjustment disc 2 is responsible for converting the horizontal movement of the hydraulic drive component 3 into the rotational movement of the gear 24 through gear and rack meshing, and realizing the synchronous rotation of the disc 21 and the gear 24, ensuring a certain synchronization accuracy. The guide vane 1 is responsible for converting the rotational movement of the synchronous adjustment disc 2 into the rotation of the blade 1, realizing the change of blade opening.

[0053] A method for adjusting a rack and pinion guide vane driven by a dual-cylinder, employing the aforementioned rack and pinion guide vane adjusting mechanism, includes the following steps:

[0054] 1. When the control signal for reducing the opening of guide vane 1 is received, the motor 402 drives the hydraulic pump 403 to rotate and pump out oil. The servo valve 414 operates in the left position T1. Part of the oil flows into the rod chamber of hydraulic cylinder A31, and the other part flows into the rodless chamber of hydraulic cylinder B35. This controls the synchronous action of hydraulic cylinder A31 retracting and hydraulic cylinder B35 extending. The rack 33 meshing with gear 24 drives gear 24 to rotate counterclockwise. The vane 13 rotates counterclockwise around the guide vane shaft 12, and the opening of guide vane 1 decreases.

[0055] 2. Upon receiving the control signal to increase the opening of guide vane 1, the motor 402 drives the hydraulic pump 403 to rotate and pump out oil. The servo valve 414 operates in its right position (T2). Part of the oil flows into the rodless chamber of hydraulic cylinder A31, and the other part flows into the rodless chamber of hydraulic cylinder B35. This controls the synchronous action of hydraulic cylinder A31 extending and hydraulic cylinder B35 retracting. The rack 33, which meshes with gear 24, drives gear 24 to rotate clockwise. The vane 13 rotates clockwise around the guide vane shaft 12, thus increasing the opening of guide vane 1.

[0056] The structure of this invention employs a gear and rack meshing connection instead of the traditional ball screw connection: abandoning the easily worn and complex maintenance of ball screw transmission methods in existing technologies, it uses a gear and rack as the core transmission pair for guide vane adjustment. Utilizing the advantages of stable linear transmission characteristics, small meshing clearance, and uniform load distribution of the gear and rack, it solves the problems of stress concentration, accelerated wear, and decreased adjustment accuracy of ball screws under high torque and high-frequency adjustment conditions. This is the core structural foundation for ensuring the synchronous adjustment accuracy of the guide vanes and the long-term reliability of the mechanism.

[0057] This invention replaces the traditional electric drive system with a hydraulic drive: overcoming the limitations of existing electric drive systems such as low power density, slow response under high torque conditions, and high locking energy consumption, by using a hydraulic system as the drive source. The key to this technology lies in leveraging the high power density, high locking strength, and fast response speed of the hydraulic system to adapt to the frequent load fluctuations and high torque output requirements of wind turbine units. Dual hydraulic cylinders drive the guide vane adjustment, effectively improving the efficiency of operating condition switching. In terms of adjustment precision, it can offset the eccentric load torque of unilateral forces, making the guide vane opening control more precise. The structural stress distribution ensures more even stress on key components such as the guide vane shaft, which is the core technical point for improving the mechanism's drive performance.

[0058] This invention also employs an integrated design of a high-precision synchronous adjustment disc: by setting an integrated synchronous adjustment disc in the guide vane adjustment mechanism, its outer edge is equipped with evenly distributed pins that precisely engage with the guide vane forks, and its inner edge is rigidly connected to gears via bosses, forming a transmission link of "gear rotation, synchronous adjustment disc linkage, and synchronous oscillation of multiple guide vanes". Through the structural integration of the synchronous adjustment disc, the linear motion of the gear rack is transformed into the synchronous rotational motion of multiple sets of guide vanes, strictly ensuring the angular consistency of the 32 sets of guide vanes, avoiding flow field turbulence and energy loss caused by asynchronous adjustment, which is the core technical guarantee for achieving high-precision synchronous adjustment of guide vanes.

[0059] This invention also employs an adaptive design that combines hydraulic drive with rack and pinion transmission: the hydraulic drive system and the rack and pinion transmission mechanism are integrated into a single design. Through a structural layout of dual-cylinder symmetrical drive rack and pinion, and high-precision meshing of the rack and pinion with the synchronous adjustment disc gear, the optimal matching of driving power and transmission efficiency is achieved. This allows the fast response characteristics of the hydraulic system and the high precision characteristics of the rack and pinion to form a synergistic effect, ultimately achieving the technical effect of "fast response, high precision, and high reliability" in guide vane adjustment. This synergistic design scheme is the core innovative combination that distinguishes this invention from existing technologies.

[0060] This invention, through the synergistic effect of the aforementioned structure and drive system, significantly improves the speed regulation accuracy and response speed of the hydraulic torque converter, ensuring a constant output speed of the speed regulation system and thus guaranteeing that the wind turbine's power generation frequency remains stable within the range required by the power grid. From a power quality perspective, this mechanism effectively reduces voltage fluctuations, frequency deviations, and harmonic content during power generation, minimizing the impact on the power grid and improving the wind turbine's grid compatibility. Simultaneously, due to the precise adjustment of the guide vanes and the efficient operation of the torque converter, the wind turbine's power generation efficiency is improved, enabling the output of more high-quality electricity under the same wind resource conditions, resulting in significant economic benefits.

[0061] In the description of this specification, references to terms such as "one embodiment," "some embodiments," "example," "specific example," or "some examples," etc., indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of the invention. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples.

[0062] Although embodiments of the present invention have been shown and described above, it is understood that the above embodiments are exemplary and should not be construed as limiting the present invention. Those skilled in the art can make changes, modifications, substitutions and variations to the above embodiments within the scope of the present invention without departing from the principles and spirit of the present invention. Any simple modifications, equivalent changes and modifications made to the above embodiments based on the technical essence of the present invention shall still fall within the scope of the technical solution of the present invention.

Claims

1. A dual-cylinder driven rack and pinion guide vane adjustment mechanism, characterized in that: Including adjustment mechanisms and hydraulic control components, The adjustment mechanism includes a guide vane (1), a synchronous adjustment disc (2), and a hydraulic drive component (3). The guide vane (1) includes a fork (11), a guide vane shaft (12), and blades (13). The blades (13) are fixed on the guide vane shaft (12). The plurality of guide vane shafts (12) are evenly arranged on the housing along the circumference, and the guide vane shafts (12) are rotatably disposed with respect to the housing. The synchronous adjustment disc (2) is rotatably disposed with respect to the housing. The synchronous adjustment disc (2) is provided with a... The pin shaft (22) is fixed at one end of the shift fork (11) to the guide vane shaft (12), and the other end of the shift fork (11) is provided with a long strip-shaped through hole, which is sleeved on the pin shaft (22). The synchronous adjustment disc (2) is also provided with a gear (24). The hydraulic drive component (3) includes a rack (33) and hydraulic cylinders A (31) and B (35) connected to both ends of the rack (33). The rack (33) meshes with the gear (24). The hydraulic control components include an oil tank (401), a motor (402), a hydraulic pump (403), and a servo valve (414). The motor (402) drives the hydraulic pump (403) to input the oil in the oil tank (401) into the servo valve (414). The output port of the servo valve (414) is connected to hydraulic cylinder A (31) and hydraulic cylinder B (35) respectively. By controlling the servo valve (414), the extension of hydraulic cylinder A (31) and the retraction of hydraulic cylinder B (35) are synchronized, or the retraction of hydraulic cylinder A (31) and the extension of hydraulic cylinder B (35) are synchronized, thereby causing the rack (33) to move and drive the synchronous adjustment disc (2) to rotate, thereby realizing the angle adjustment of the guide vane (1).

2. The dual-cylinder driven rack and pinion guide vane adjustment mechanism according to claim 1, characterized in that, The synchronous adjustment disc (2) includes a disc (21) and a boss (23). The pin (21) is located on the outer edge of one side of the disc (21), the boss (23) is located on the inner edge of one side of the disc (21), and the gear (24) is located on the boss (23).

3. The dual-cylinder driven rack and pinion guide vane adjustment mechanism according to claim 1, characterized in that, The hydraulic rod A (32) of the hydraulic cylinder A (31) is fixedly connected to one end of the rack (33), and the other end of the rack (33) is fixedly connected to the hydraulic rod B (34) of the hydraulic cylinder B (35).

4. The dual-cylinder driven rack and pinion guide vane adjustment mechanism according to claim 1, characterized in that, The servo valve (414) and the hydraulic pump (403) are connected in sequence by a check valve (406) and a filter device (407), and the filter device (407) integrates an alarm device.

5. The dual-cylinder driven rack and pinion guide vane adjustment mechanism according to claim 4, characterized in that, A bypass oil circuit is provided between the filter device (407) and the servo valve (414) and connected to the accumulator (413). A switching valve (410) and a shut-off valve (412) are also provided on the bypass oil circuit, and a pressure flow sensor (411) is provided between the switching valve (410) and the shut-off valve (412).

6. The dual-cylinder driven rack and pinion guide vane adjustment mechanism according to claim 1, characterized in that, The hydraulic pump (403) and the servo valve (414) are also provided with a return oil pipeline connected to the oil tank (401), and the return oil pipeline is provided with a switch valve (408), an overflow valve (409) and a cooling device (404).

7. The dual-cylinder driven rack and pinion guide vane adjustment mechanism according to claim 6, characterized in that, The cooling device (404) includes a cooling motor, a fan and a cooler. The oil in the return oil pipeline flows back to the oil tank (401) through the cooler. The cooling motor drives the fan to rotate and dissipate the heat of the oil inside the cooler.

8. The dual-cylinder driven rack and pinion guide vane adjustment mechanism according to claim 1, characterized in that, Hydraulic cylinders A (31) and B (35) are both equipped with displacement sensors (417). Hydraulic cylinder A (31) is also equipped with a limit switch A (418), and hydraulic cylinder B (35) is also equipped with a limit switch B (419). The servo valve (414) controls the position of hydraulic rod A (32) of hydraulic cylinder A (31) and hydraulic rod B (34) of hydraulic cylinder B (35) according to the signals from displacement sensor (417), limit switch A (418) and limit switch B (419).

9. The dual-cylinder driven rack and pinion guide vane adjustment mechanism according to claim 1, characterized in that, The oil tank (401) is also equipped with auxiliary components, including a thermometer for monitoring the temperature of the oil inside the oil tank (401), a filter for monitoring the cleanliness of the oil inside the oil tank (401), and a level gauge for monitoring the level of the oil inside the oil tank (401).

10. A method for adjusting a rack and pinion guide vane driven by a dual-cylinder engine, characterized in that, The dual-cylinder driven rack and pinion guide vane adjustment mechanism according to any one of claims 1 to 9 comprises the following steps: (1) When the control signal for reducing the opening of the guide vane (1) is received, the motor (402) drives the hydraulic pump (403) to rotate and pump out oil. The servo valve (414) operates in the left position T1. Part of the oil flows into the rod chamber of the hydraulic cylinder A (31), and the other oil flows into the rodless chamber of the hydraulic cylinder B (35). The synchronous action of the hydraulic cylinder A (31) retracting and the hydraulic cylinder B (35) extending is controlled respectively. The rack (33) meshing with the gear (24) drives the gear (24) to rotate counterclockwise. The blade (13) rotates counterclockwise around the guide vane shaft (12), and the opening of the guide vane (1) decreases. (2) When the control signal for increasing the opening of the guide vane (1) is received, the motor (402) drives the hydraulic pump (403) to rotate and pump out oil. The servo valve (414) operates in the right position T2. ​​Part of the oil flows into the rodless chamber of hydraulic cylinder A (31), and the other part flows into the rodless chamber of hydraulic cylinder B (35). The synchronous action of hydraulic cylinder A (31) extending and hydraulic cylinder B (35) retracting is controlled respectively. The rack (33) meshing with the gear (24) drives the gear (24) to rotate clockwise. The blade (13) rotates clockwise around the guide vane shaft (12), and the opening of the guide vane (1) increases.

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