Single-cylinder-driven rope row linkage telescopic tower and wind condition self-adaptive regulation and control method

Abstract

The application discloses a single-cylinder driving rope row linkage telescopic tower drum and a wind condition self-adaptive regulation and control method, and belongs to the technical field of wind power tower drum equipment. The tower drum comprises a fixed drum body, a first telescopic drum body and a second telescopic drum body, and constitutes a three-stage coaxial nested structure. A single cylinder is used as the only active driving source, and the output rod of the cylinder is connected with the first telescopic drum body. A linkage assembly is formed by a pulley block installed on the first telescopic drum body and a traction rope, the first end of the traction rope is fixed to the fixed drum body, the second end is fixed to the second telescopic drum body, and the second telescopic drum body is synchronously telescoped in the same direction with a stroke twice that of the first telescopic drum body by using the principle of a movable pulley. The single cylinder is used to drive a two-stage linkage, the structure is simple, the synchronization precision is high, and the wind energy utilization rate and operation safety can be remarkably improved.

Description

Technical Field

[0001] This invention belongs to the technical field of wind power tower equipment, specifically relating to a telescopic tower with single electric cylinder driving rope linkage, and a wind condition adaptive control method for the tower. Background Technology

[0002] The wind turbine tower is the core load-bearing support component of a wind turbine generator, and its height directly affects wind energy capture efficiency and the operational safety of the unit. Traditional wind turbine towers mostly adopt a one-piece fixed-height structure, which cannot flexibly adjust the operating height according to the complex and ever-changing wind field conditions. This results in prominent problems such as insufficient wind energy utilization under low wind speed conditions and excessive structural load under high wind speed conditions.

[0003] To address the aforementioned issues, various height-adjustable tower solutions have emerged in recent years. For example, Chinese invention patent CN109306938A (hereinafter referred to as D1) discloses a wind turbine tower that employs a multi-section telescopic tower, with each section independently supported and driven by multiple hydraulic cylinders distributed along the circumference. Although this solution achieves height adjustment, it suffers from the following shortcomings: (1) Each section requires multiple hydraulic cylinders for independent drive, resulting in a complex system and high cost; (2) There is a lack of mechanical linkage between the multiple hydraulic cylinders, and the lifting of each section relies on the synchronous control of the hydraulic system. In actual operation, the synchronization accuracy is affected by the flow distribution and pressure fluctuations of the hydraulic system, which can easily lead to uneven loading and jamming. The typical synchronization accuracy is approximately ±5mm; (3) The hydraulic system's performance degrades in low-temperature environments, and there is a risk of leakage during long-term operation, resulting in high maintenance costs.

[0004] US Patent 2008 / 0236060 A1 (hereinafter referred to as D2) discloses a telescopic tower system that uses a winch-driven cable system to raise and lower the tower, and synchronizes the extension and retraction of each segment via synchronous cables. The transmission path of this scheme is "winch → long cable → pulling the top segment," which is a "pull" transmission method, meaning the top segment is the active traction end, and the intermediate segments passively follow via synchronous cables. In this scheme, the drive cable must bear the entire extension load of the tower, and the cable's load-bearing capacity directly limits the tower's height and weight. When applied to heavy-load scenarios, the elastic deformation and plastic elongation of the long-distance cable will significantly affect positioning accuracy and structural safety. The following shortcomings exist in this scheme: (1) The winch and cable system has a complex structure and requires a large number of pulleys and cables, which occupy the internal space of the tower; (2) The drive source is located at the bottom winch, which pulls the top section through a long-distance cable. The cable is prone to plastic deformation and fatigue under long-term load, which affects the positioning accuracy and reliability; (3) This scheme was originally designed for lightweight scenarios such as portable monitoring towers. The cable has limited load-bearing capacity. When applied to heavy-duty wind power towers, the load-bearing capacity and durability of the cable system are insufficient.

[0005] Chinese utility model patent CN201560900U (hereinafter referred to as D3) discloses a liftable tower for a small wind turbine, which adopts a sleeve rod segmented interlocking structure. The inner sleeve is raised by manually pulling down the iron chain cable, and the positioning rod is inserted into the positioning hole to lock it. The structure of this solution is simple, but it has the following shortcomings: (1) It is manually operated and cannot achieve automatic wind condition adaptive control; (2) The positioning hole is a discrete stepped locking, which cannot achieve accurate positioning at any height; (3) There is no dedicated guiding mechanism. The lifting process relies only on the gap between the sleeves for guidance, which is prone to shaking and deviation; (4) There is no structure for folding down for maintenance. Maintenance still requires high-altitude or hoisting operations.

[0006] As can be seen from the existing technologies described above, there are two main technical paths in this field: one is the path represented by D1, which involves independent drive of multiple hydraulic cylinders combined with hydraulic synchronous control. The technical improvement direction of this path lies in optimizing the control accuracy and synchronization algorithm of the hydraulic system; the other is the path represented by D2, which involves a winch combined with cable pulling. This path is limited by the cable's load-bearing capacity and long-distance transmission accuracy, and is mostly used for lightweight towers. Under the technical framework of D1, in order to solve the problem of insufficient synchronization accuracy of multiple hydraulic cylinders, those skilled in the art usually make improvements from the perspective of optimizing the hydraulic system (such as using high-precision proportional servo valves and improving the synchronization control algorithm). However, the pulling transmission method of D2 determines that its drive cable must bear the entire telescopic load. When the weight of the tower increases, the elastic deformation and load-bearing safety of the cable become insurmountable technical obstacles. Therefore, the D2 solution is difficult to directly apply to heavy-load wind power tower scenarios. If the cable synchronization method of D2 is combined with the multi-section tower of D1, it is still necessary to solve the problems of load distribution and maintaining positioning accuracy of the cable under heavy-load conditions. There is a lack of existing technologies that can overcome the inherent limitations of the two aforementioned technical paths and effectively integrate drive simplification with high precision.

[0007] Furthermore, in this field, the guide structures of liftable towers are mostly exposed, constantly exposed to harsh outdoor environments of wind, sand, rain, snow, and alternating high and low temperatures. This makes them prone to corrosion, scale buildup, and wear, and long-term operation can easily lead to malfunctions such as lifting jamming and positioning misalignment. At the same time, existing towers generally rely heavily on large hoisting equipment and high-altitude operations during installation and maintenance, resulting in high construction difficulty, high costs, and high maintenance risks. These problems are not limited to a single comparative document, but rather represent long-standing and widespread technical pain points in this field.

[0008] In summary, the existing technology lacks a retractable tower solution that systematically integrates functions such as simplified drive, linkage synchronization, guidance and dust prevention, multi-point locking, and collapse maintenance. There is an urgent need to provide an overall solution that is simple in structure, has high synchronization accuracy, reliable in operation, and is easy to maintain. Summary of the Invention

[0009] This invention overcomes the shortcomings of existing technologies and provides a telescopic tower with a single electric cylinder driving a rope linkage and a wind-adaptive control method. The single electric cylinder serves as the sole active drive source for raising and lowering the telescopic tower. The motion is simultaneously transmitted to both stages of the telescopic tower via a rope linkage assembly. Utilizing the principle of a movable pulley, the stroke of the second telescopic tower is twice that of the first, achieving high-precision synchronous raising and lowering of the two stages. This simplifies the drive structure and fundamentally eliminates hydraulic synchronization errors. Combined with a guide mechanism, locking mechanism, hinged folding mechanism, and cable-stayed stabilization structure, it addresses the issues of dust prevention during lifting and guiding, redundant positioning safety, and convenient maintenance, forming a comprehensive solution that balances power generation efficiency, operational safety, and convenient maintenance.

[0010] To solve the above-mentioned technical problems, the technical solution adopted by the present invention is as follows: a telescopic tower cylinder driven by a single electric cylinder and linked by a rope, comprising a fixed cylinder body, a first telescopic cylinder body, a second telescopic cylinder body, an electric cylinder, and a linkage assembly.

[0011] The fixed cylinder serves as a basic load-bearing component and is fixedly installed on the foundation or base (such as a concrete foundation or a steel structure base).

[0012] The first telescopic cylinder is slidably sleeved inside the fixed cylinder, forming the first-stage movable telescopic unit.

[0013] The second telescopic cylinder is slidably fitted inside the first telescopic cylinder to form a second-stage movable telescopic unit; the top of the second telescopic cylinder is used to install the nacelle and blade assembly.

[0014] The cylinder body of the electric cylinder is fixed to the fixed cylindrical body, and its output rod is connected to the first telescopic cylindrical body to drive the first telescopic cylindrical body to move axially. The electric cylinder is preferably a servo multi-stage electric cylinder with closed-loop position control; alternatively, a stepper electric cylinder or a regular electric cylinder can be used, as long as it can provide linear reciprocating motion.

[0015] The linkage assembly includes a pulley system mounted on the first telescopic cylinder and a traction rope that passes around the pulley system. The first end of the traction rope is fixedly connected to the fixed cylinder, and the second end is fixedly connected to the second telescopic cylinder. The pulley system and the traction rope are arranged around the periphery of the electric cylinder. The traction rope runs along the annular space between the inner wall of the cylinder and the electric cylinder, parallel to the electric cylinder and without interference. The total length of the traction rope matches the initial installation position of each stage of the cylinder. In the lowest retracted state, the traction rope is in a pre-tensioned state. This pre-tensioned state is a crucial initial condition for ensuring the strict validity of the moving pulley principle: if the traction rope is slack in the initial state, the slack in the rope segment must be eliminated before the electric cylinder starts, resulting in the actual displacement of the second telescopic cylinder being less than twice the displacement of the first telescopic cylinder; through pre-tensioning, the traction rope can be kept taut throughout the entire lifting and lowering process, thereby ensuring that the stroke of the second telescopic cylinder is precisely twice the stroke of the first telescopic cylinder.

[0016] Based on the above structure, when the electric cylinder drives the first telescopic cylinder to rise a distance L, the pulley block mounted on the first telescopic cylinder moves upward by L accordingly. Since the first end of the traction rope is fixed to the fixed cylinder (stationary), the rope length from the fixed end to the pulley block increases by L; to keep the rope length constant, the rope length from the pulley block to the second end of the traction rope shortens by L, that is, the second telescopic cylinder rises L relative to the first telescopic cylinder, and its base has also risen L with the first telescopic cylinder. Therefore, the total displacement of the second telescopic cylinder relative to the fixed cylinder is 2L. This achieves synchronous telescopic extension and retraction of the two-stage telescopic cylinders at a 1:2 stroke ratio. The descent process is similar.

[0017] The transmission path of this invention is electric cylinder → first telescopic cylinder (active) → pulley block → traction rope → second telescopic cylinder (passive), forming a series mechanical linkage. The electric cylinder push rod bears the main load, and the traction rope only transmits the load of the second telescopic cylinder and its components. The stress conditions are significantly better than the full-load cable scheme, which fundamentally ensures transmission accuracy and load-bearing reliability.

[0018] To ensure the verticality and stability of the tower's lifting and lowering, and to provide geometric constraints for precise synchronization of the rope linkage, the telescopic tower preferably includes a guide mechanism. The guide mechanism includes a closed guide groove disposed on the inner wall of the fixed tower and a guide slider disposed on the outer wall of the first telescopic tower. The guide slider is embedded in the guide groove to form a sliding fit. To adapt to harsh outdoor environments, a sealing brush strip is installed at the opening of the closed guide groove to prevent external impurities such as wind, sand, and rainwater from entering the guide groove and to avoid lifting and lowering jams caused by dust accumulation and corrosion.

[0019] To improve the positioning reliability of the tower at the target height, preferably, the telescopic tower also includes a locking mechanism. The locking mechanism matches the stepless telescopic characteristic of the aforementioned rope linkage, enabling multi-point continuous locking at any height. The locking mechanism is located between the fixed cylinder and the first telescopic cylinder, used to lock the position of either the first or second telescopic cylinder after it has moved into place. Further, the locking mechanism includes a mechanical locking assembly, which includes multiple locking teeth arranged axially along the first telescopic cylinder and locking claws disposed on the fixed cylinder. The locking claws can engage with the gaps between the locking teeth to achieve locking. Even further, to form redundant protection, the electric cylinder is a servo electric cylinder, and the locking mechanism also includes an electrical locking device integrated inside the electric cylinder, which is the brake of the servo electric cylinder.

[0020] For ease of installation and maintenance, preferably, the lower end of the fixed cylinder is equipped with a hinge pin for hinged connection to the foundation, allowing the retractable tower to rotate between upright and horizontal positions around the hinge pin. This tilting function works in conjunction with the tower's retractable characteristics; that is, before tilting, the tower is retracted to its lowest storage height, significantly reducing the tilting center of gravity and overturning moment. To further enhance stability in upright conditions, multiple sets of stay cables are included. One end of each stay cable is connected to the fixed cylinder, and the other end is anchored to the foundation. At least one set of stay cables is arranged parallel to the axial direction of the hinge pin, so that this set of stay cables can be released when the tower is tilted to prevent motion interference. The remaining stay cables are simultaneously relaxed and unloaded during the tilting process, ensuring a smooth and controllable tilting process. In upright conditions, the simultaneous tensioning of multiple sets of stay cables can effectively counteract lateral wind loads and overturning moments, suppressing wind-induced swaying of the tower.

[0021] To achieve automated control, preferably, the telescopic tower also includes a control system, which includes a wind speed and direction sensor and a main control unit. The main control unit is connected to the wind speed and direction sensor and the electric cylinder signal, respectively, and is used to control the telescopic movement of the electric cylinder according to the wind speed data collected by the wind speed and direction sensor.

[0022] This invention also provides a wind-adaptive control method for a telescopic tower with a single electric cylinder driving a rope system, comprising the following steps: S1: Obtain real-time wind speed data through wind speed and direction sensors; S2: Based on the wind speed data, control the electric cylinder of the telescopic tower to operate, and drive the first telescopic cylinder and the second telescopic cylinder to extend and retract synchronously via the linkage component to adjust the tower height, wherein the travel distance of the second telescopic cylinder is twice the travel distance of the first telescopic cylinder; wherein the cylinder body of the electric cylinder is fixed to the fixed cylinder, and the output rod is connected to the first telescopic cylinder; the linkage component includes a pulley group installed on the first telescopic cylinder and a traction rope passing over the pulley group, wherein the first end of the traction rope is fixedly connected to the fixed cylinder, and the second end is fixedly connected to the second telescopic cylinder.

[0023] Preferably, in step S2: when the wind speed data is lower than a preset first threshold, the electric cylinder is controlled to extend, so that the tower is raised to the highest working height to maximize the capture of high-altitude wind energy; when the wind speed data is higher than a preset second threshold, the electric cylinder is controlled to retract, so that the tower is lowered to the lowest working height to reduce wind load and achieve active unloading protection.

[0024] Preferably, in step S2: when the wind speed data is between the first threshold and the second threshold, a PID control algorithm is used to dynamically adjust the extension and retraction of the electric cylinder to keep the blades within the target height range and ensure stable output power; wherein, the target height range is the height range with the smallest wind speed fluctuation and the most stable wind direction. This range can be determined by wind speed gradient measurement or historical wind data statistics. Wind speed gradient measurement is to measure the wind speed profile in real time using anemometers installed at different heights, and historical wind data statistics is to establish a height-wind speed statistical model based on long-term wind field measurement data.

[0025] Preferably, the telescopic tower also includes a locking mechanism; the control method further includes: controlling the locking mechanism to unlock before controlling the electric cylinder to work; and controlling the locking mechanism to lock after the tower height is adjusted to the correct position.

[0026] Preferably, the control method further includes a down-and-maintenance step: controlling the tower to retract to its lowest height; locking the blades; loosening a group of stay cables whose arrangement direction is parallel to the axial direction of the hinge pin, simultaneously relaxing the remaining stay cables to relieve stress, and using the hinge pin as a fulcrum, lowering the tower to a flat position on the ground for maintenance; after maintenance is completed, standing the tower upright and resetting it, tensioning the stay cables, and restoring the operating conditions.

[0027] The beneficial effects of this invention compared to the prior art are: 1. This invention utilizes a single electric cylinder drive in conjunction with a rope linkage assembly, employing the principle of a moving pulley to achieve a two-stage series mechanical linkage with a 1:2 stroke ratio. This solidifies the motion relationship between the two-stage telescopic cylinders into a defined mechanical transmission ratio, eliminating the asynchronous error source of multiple cylinders from the transmission principle. This mechanical linkage method is unaffected by changes in hydraulic oil temperature and viscosity. Under rated operating conditions, the synchronization deviation of the two stages can be controlled within ±1mm, significantly outperforming multi-hydraulic cylinder solutions that rely on hydraulic synchronization control. Furthermore, this invention completely avoids inherent defects such as hydraulic system leakage and difficulty in low-temperature starting, reducing failure rates and maintenance costs. Compared to the D2 solution that uses a winch to pull the top section via a long-distance cable, this invention employs a series linkage method of pushing the middle cylinder and then the inner cylinder. This results in a shorter traction rope path that transmits only the second-stage load, leading to less cumulative elastic deformation and superior positioning accuracy.

[0028] 2. This invention uses a closed guide groove and a guide slider with high-precision sliding cooperation to limit the horizontal offset and radial sway of the telescopic cylinder in the circumferential direction, providing a stable geometric constraint for the precise synchronization of the rope linkage; the sealing brush strip set at the groove opening can prevent external impurities such as wind, sand and rainwater from entering the groove, avoiding the dust accumulation and corrosion and lifting jamming problems caused by the exposed layout of the existing liftable tower guide structure, and ensuring the guiding accuracy and lifting stability during long-term operation.

[0029] 3. This invention establishes a dual-redundancy protection system through a mechanical locking assembly (locking teeth and locking claws engaging) positioned between the fixed cylinder and the first telescopic cylinder, and an electrical locking device (holding brake) integrated inside the servo cylinder. During normal operation, the mechanical locking bears the vertical static load of the tower, while the electrical holding brake provides supplementary braking force. In extreme conditions where either locking element fails, the other element can still independently bear the load, fundamentally eliminating the risk of slippage and fall that may occur with a single locking scheme, and significantly improving the operational reliability of the tower.

[0030] 4. The control system of the present invention uses real-time wind speed data as feedback signal and adopts PID algorithm to close-loop adjust the extension and retraction of the electric cylinder, which can quickly and accurately execute height adjustment commands; under low wind speed conditions, the power generation efficiency is improved by raising the height, and under high wind speed conditions, the wind load is reduced by lowering the height, thus achieving a dynamic balance between wind energy capture and load control.

[0031] 5. This invention utilizes the principle of movable pulleys to achieve a 1:2 stroke ratio, enabling a 2L effective extension / retraction of the second telescopic cylinder in heavy-duty, long-stroke applications such as wind turbine towers, while maintaining an electric cylinder stroke of L. Taking Example 1 as an example, the effective stroke of the second telescopic cylinder is 16m, while the electric cylinder stroke is only 8m, which is half the length of the electric cylinder stroke compared to the direct drive solution. This significantly reduces the selection threshold and manufacturing cost of long-stroke, heavy-duty electric cylinders.

[0032] 6. This invention utilizes a design that combines a hinged pin at the lower end of the fixed tower with multiple sets of stay cables. Before lowering the tower, it retracts to its lowest possible height to lower the center of gravity, allowing for flat ground maintenance of the entire unit. This eliminates the need for large hoisting equipment and completely avoids the risks of working at heights. Compared to traditional fixed tower maintenance methods that require large hoisting equipment and take approximately 3 days per maintenance session, this invention reduces the time to 1 day per session, improving maintenance efficiency by approximately 60%.

[0033] 7. This invention uses a single electric cylinder combined with rope linkage as the core transmission scheme. It features a simple structure and unified control logic. From small-power units to large-power units, only the cylinder diameter / wall thickness and electric cylinder thrust / stroke parameters need to be adjusted according to the load level, while the core transmission principle and control system architecture remain unchanged. As shown in the parameter adaptation of Examples 1 (200kW), 2 (1.5MW) to 4 (3MW), this invention has good feasibility across multiple power levels and significant application value. Attached Figure Description

[0034] The present invention will now be further described with reference to the accompanying drawings.

[0035] Figure 1 This is a schematic diagram of the entire machine in a horizontal maintenance state. Figure 2 This is a schematic diagram of the tower's vertical position at its lowest storage height according to the present invention. Figure 3 This is a schematic diagram of the tower in its upright position at the middle height of the present invention; Figure 4 This is a schematic diagram of the tower section of the present invention in its upright state with the maximum extension height. Figure 5 This is a cross-sectional view of the internal structure of the retractable tower in this invention; Figure 6 for Figure 5 A partially enlarged schematic diagram of the locking mechanism at point A; Figure 7 for Figure 5 A partially enlarged schematic diagram of the upper pulley block and rope drive structure at part B; Figure 8 for Figure 5 A partially enlarged schematic diagram of the lower pulley block and rope drive structure at section C.

[0036] In the diagram: 1 is the fixed cylinder; 2 is the first telescopic cylinder; 3 is the second telescopic cylinder; 4 is the electric cylinder; 5 is the traction rope; 6 is the pulley block; 8 is the enclosed guide groove; 9 is the guide slider; 10 is the locking tooth; 11 is the locking claw; 12 is the wind speed and direction sensor; 13 is the hinge pin; 14 is the stay cable. Detailed Implementation

[0037] The present invention will be further described in detail below with reference to the accompanying drawings and embodiments. The following embodiments are for illustrative purposes only and should not be considered as limiting the scope of the invention.

[0038] Example 1, as Figures 1 to 8 As shown, this embodiment is adapted to a horizontal axis wind turbine with a rated power of 200kW. It adopts a three-stage telescopic structure, with a maximum tower height of 34m (excluding the nacelle and blade assembly; the maximum operating height is the tower height plus the dimensions of the nacelle and blade assembly, approximately 36-37m), and a minimum retractable height of 10m. In this embodiment, the minimum retractable height is the same as the minimum operating height, both being 10m.

[0039] I. Main Structure and Material Parameters of the Tower The overall structure comprises a three-stage coaxial nested structure consisting of a fixed cylinder 1, a first telescopic cylinder 2, and a second telescopic cylinder 3. The fixed cylinder 1 is a stationary foundation support component, fixedly installed on a foundation or base. The first telescopic cylinder 2 is nested inside the fixed cylinder 1, forming the first-stage movable telescopic unit. The second telescopic cylinder 3 is nested inside the first telescopic cylinder 2, with the nacelle and blade assembly mounted at its top, forming the second-stage movable telescopic unit. Sliding clearances are provided between each stage of the cylinder.

[0040] Each cylinder is made of Q355D low-alloy high-strength structural steel, and adopts a conical structure to optimize stress performance and wind resistance stability. Fixed cylinder 1: bottom outer diameter Φ2200mm, top outer diameter Φ1800mm, wall thickness 20mm, total height 10m; First telescopic cylinder 2: bottom outer diameter Φ1750mm, top outer diameter Φ1500mm, wall thickness 16mm, effective stroke 8m; Second telescopic cylinder 3: bottom outer diameter Φ1450mm, top outer diameter Φ1200mm, wall thickness 14mm, effective stroke 16m.

[0041] The fixed cylinder 1 has a height of 10m. The effective stroke of the first telescopic cylinder 2 is 8m. The effective stroke of the second telescopic cylinder 3 is 16m (twice the stroke of the first telescopic cylinder). The maximum height of the tower top is 34m, and the minimum retracted height is 10m (when both telescopic cylinders are fully retracted).

[0042] II. Electric Cylinder and Linkage Components The electric cylinder 4 is vertically fixedly installed at the center of the fixed cylinder 1. The bottom end of the cylinder is rigidly connected to the bottom base of the fixed cylinder 1 by flange bolts. The top end of the telescopic push rod is connected to the bottom bearing plate of the first telescopic cylinder 2 by a flange. The electric cylinder 4 is a servo multi-stage electric cylinder with the following main parameters: stroke 8m, rated thrust 160kN, rated speed 0.15m / s, repeatability ±0.2mm, protection level IP67, working mode S1 (continuous working mode), built-in absolute position encoder for position closed-loop control, and built-in holding brake for electrical locking.

[0043] The linkage assembly includes a pulley block 6 and a traction rope 5 installed on the upper part of the first telescopic cylinder 2. In this embodiment, the pulley block 6 includes two fixed pulleys, symmetrically arranged on both sides of the upper part of the first telescopic cylinder 2 (180° symmetrical), and fixed to the pulley mounting bracket by a pin. The mounting bracket is welded to the inner wall of the first telescopic cylinder 2.

[0044] The traction rope 5 is a high-strength galvanized steel wire rope with the following parameters: diameter 16mm, structure 6×36WS, nominal tensile strength 1770MPa, and minimum breaking strength ≥200kN. The traction rope 5 uses a single wire rope S-shaped winding method, passing through two fixed pulleys: the first end is fixed to the anchoring lug on the top inner side of the fixed cylinder 1 via a rope end wedge joint; the wire rope extends downwards, passes over the first fixed pulley, then upwards, passes over the second fixed pulley on the symmetrical side, and then extends downwards again, with the second end fixed to the anchoring lug at the bottom bearing end of the second telescopic cylinder 3 via a rope end wedge joint. This S-shaped winding method achieves balanced force distribution on both sides of the first telescopic cylinder. Both the pulley block 6 and the traction rope 5 are arranged around the electric cylinder 4. The traction rope 5 runs along the annular space between the inner wall of the fixed cylinder 1 and the electric cylinder 4, parallel to the electric cylinder 4 and without interference.

[0045] The total length of the traction rope 5 is matched with the initial installation position of each stage of the cylinder. In the lowest retracted state, the traction rope 5 is in a pre-tensioned state. The pre-tension force is set to 5% to 8% of the minimum breaking strength of the wire rope, which is about 10 to 16 kN in this embodiment.

[0046] With the above arrangement, when the electric cylinder 4 drives the first telescopic cylinder 2 to rise a distance L, the pulley block 6 installed on the first telescopic cylinder 2 moves upward by L accordingly. Since the first end of the traction rope 5 is fixed to the top of the fixed cylinder 1 (fixed), the rope length from the fixed end to the pulley block 6 increases by L; to keep the rope length constant, the rope length from the pulley block 6 to the second end of the traction rope 5 is shortened by L, that is, the second telescopic cylinder 3 rises L relative to the first telescopic cylinder 2, and the total displacement relative to the fixed cylinder 1 is 2L. Therefore, when the first telescopic cylinder 2 rises 8m, the second telescopic cylinder 3 rises 16m synchronously, with a total telescopic amount of 24m for both stages, and the tower top rises from a minimum of 10m to a maximum of 34m. The descent process is the same. This achieves synchronous telescopic movement of two stages driven by a single electric cylinder at a stroke ratio of 1:2.

[0047] III. Guiding Mechanism The guiding mechanism includes closed guide grooves 8 vertically and symmetrically arranged on the inner wall of the fixed cylinder 1, and guide sliders 9 correspondingly arranged on the outer wall of the first telescopic cylinder 2. In this embodiment, four sets of guide grooves 8 are evenly arranged circumferentially along the inner wall of the fixed cylinder 1 (spaced 90° apart from each other), and four sets of guide sliders 9 are correspondingly arranged.

[0048] The closed guide groove 8 is fixed to the inner wall of the fixed cylinder 1 by welding. The bottom of the groove fits against the inner wall of the cylinder. The inner cross-section of the groove is rectangular (60mm wide and 70mm deep), and the groove opening is 25mm wide. The guide surfaces on both sides are precision machined to a surface roughness Ra≤1.6μm. The guide slider 9 is made of wear-resistant bronze (CuSn10P1) and is fixed to the slider mounting seat on the outer wall of the first telescopic cylinder 2 by bolts. The slider's shape matches the inner cavity of the groove (55mm wide and 65mm deep), and it is embedded in the guide groove 8 to form a high-precision sliding fit (0.3~0.5mm clearance on one side), which restricts the horizontal offset and radial sway of the first telescopic cylinder 2 in the circumferential direction.

[0049] Wear-resistant sealing brush strips are installed on both sides of the groove opening of the closed guide slide 8. They are clamped and fixed by aluminum alloy pressure plates. The brush ends keep in contact with the surface of the guide slider 9, which can remove sand and dust attached to the surface of the slider and prevent external rain, snow and sand from entering the interior of the slide.

[0050] IV. Locking Mechanism The locking mechanism employs a dual locking system. A set of locking teeth 10 (i.e., locking tooth discs) is arranged vertically at 8cm intervals on the outer wall of the first telescopic cylinder 2, forming a continuous and uniform tooth surface along the axial direction (approximately 100 locking points in total). The locking teeth 10 are a split structure, fixed to an annular mounting base on the outer wall of the first telescopic cylinder 2 by bolts. They are made of 42CrMo alloy steel, with surface hardening treatment (hardness HRC48~52), trapezoidal tooth shape (tooth angle 30°), and tooth depth 6mm.

[0051] Locking claws 11 (one per 90° direction, four in total) are hinged to the inner side of the upper part of the fixed cylinder 1. The claws are also made of 42CrMo (surface hardened to HRC48-52) and are hinged to the claw bracket on the inner wall of the fixed cylinder 1 via pins. An elastic clamping assembly (in this embodiment, a helical compression spring with a spring stiffness of 100 N / mm and a pre-compression of 20 mm) is fitted to the tail of the claw. As the first telescopic cylinder 2 rises and falls, the claws 11 remain in contact with the tooth surface under the action of the elastic clamping assembly. During rising and falling, the claws slide along the tooth surface and automatically fall into the tooth gap.

[0052] Once the tower reaches the target height, the elastic clamping assembly pushes the locking claw 11 to rotate, and the locking teeth adaptively engage with the corresponding locking teeth 10, achieving multi-point height locking with centimeter-level precision. During unlocking, the control system controls the electromagnet to drive the claw 11 to overcome the spring force and disengage from the toothed disc.

[0053] Meanwhile, the electric cylinder 4 has a built-in servo motor brake (power-off braking type, braking torque ≥ 3 times the rated load torque). After the output stops, the brake automatically locks the motor output shaft, maintaining the push rod position. The mechanical lock bears the main load (vertical static load, designed load capacity not less than 20t / claw), while the electric brake serves as a backup protection (to prevent the electric cylinder from accidentally retracting), providing double protection to eliminate the risk of slippage and fall.

[0054] V. Control System The control system includes a high-precision wind speed and direction sensor 12 installed on the upper end of the second telescopic cylinder 3 (see...). Figure 4 (Note) and the main control unit. The main control unit is electrically connected to the wind speed and direction sensor 12, the electric cylinder 4, and the locking mechanism, and has built-in wind speed segmented control logic.

[0055] The wind speed and direction sensor 12 has the following parameters: wind speed detection accuracy ±0.1m / s, wind direction detection accuracy ±3°, heated and de-iced type, suitable for low-temperature environments down to -40℃. The core control chip of the main control unit is an industrial-grade PLC (Siemens S7-1200 or equivalent), featuring multiple analog inputs, digital input / output interfaces, and PID closed-loop control. The main control unit controls the extension and retraction speed and position of the electric cylinder 4 via a servo driver, and controls the unlocking and locking actions of the locking claw 11 via a relay-controlled electromagnet.

[0056] The specific logic for segmented wind speed control is as follows: When the real-time wind speed is in the low wind speed range of 3-6 m / s, the main control unit determines it to be a weak wind condition. First, it controls the locking claw 11 to disengage from the locking tooth 10 to complete the unlocking, and then drives the electric cylinder 4 to extend smoothly to the maximum stroke (8m) at a speed of 0.12m / s. Through the linkage component, it drives the first telescopic cylinder 2 to rise by 8m and the second telescopic cylinder 3 to rise by 16m, raising the tower top to the maximum height of 34m, maximizing the capture of high-altitude wind energy.

[0057] When the real-time wind speed is within the optimal operating range of 6–8 m / s, the main control unit determines it to be in the optimal operating condition. The main control unit uses the wind speed signal collected by the wind speed and direction sensor 12 as feedback, and employs a PID algorithm to dynamically fine-tune the extension and retraction of the electric cylinder 4 (typical PID parameters: proportional gain Kp = 1.2, integral time Ti = 2.5 s, derivative time Td = 0.3 s). This allows for real-time adjustment of the tower height, ensuring the blades are always maintained within a height range where wind speed is stable and wind force is uniform (i.e., the height range with the least wind speed fluctuation and the most stable wind direction, determined through wind speed gradient measurement or historical wind data statistics), thus guaranteeing stable unit output power.

[0058] When the real-time wind speed exceeds 8 m / s, the main control unit determines it to be a high-wind-speed condition. The electric cylinder 4 retracts smoothly at a speed of 0.10 m / s, driving the first telescopic cylinder 2 to descend and the second telescopic cylinder 3 to descend synchronously at twice the speed via the linkage components. This lowers the overall height and center of gravity, reducing the blade's frontal area and the overall wind load. Once the wind speed returns to a safe range, it automatically adjusts back to a suitable height.

[0059] After the height is adjusted to the correct position, the main control unit controls the locking claw 11 to automatically engage with the corresponding locking tooth 10 under the action of the elastic clamping component, and at the same time triggers the electric cylinder 4 to hold the brake and lock, thus completing the height fixation.

[0060] The above control process constitutes a complete control link of "perception (sensor) → decision (main control unit PID algorithm) → execution (electric cylinder extension and retraction) → feedback (sensor closed loop)", with a settling time of ≤3s.

[0061] VI. Hinged and Cable-stayed Structures The bottom end of the fixed cylinder 1 is hinged to the wind turbine foundation via a hinge pin 13, allowing the entire unit to rotate 0° to 90° around the pin. The hinge pin 13 is made of 40CrNiMoA high-strength alloy steel (diameter Φ120mm, heat-treated HB280~320). Four sets of inclined stay cables 14 (each set consisting of two parallel steel strands) are evenly distributed circumferentially on the lower part of the fixed cylinder 1, arranged symmetrically in a rectangular four-way configuration (from top view). Figure 8 The middle section is located at 0°, 90°, 180°, and 270° respectively, and the end is anchored to the pre-set anchor points around the foundation by ground anchor bolts.

[0062] The stay cables 14 are made of high-strength, low-relaxation steel strands with the following specifications: 1×7 structure, nominal diameter 15.2mm, tensile strength 1860MPa, and equipped with adjustable-length turnbuckles for easy tension adjustment. Under upright conditions, all four stay cables 14 are simultaneously tensioned to the design preload (15t per cable in this embodiment), effectively counteracting the overturning moment caused by lateral wind loads, suppressing tower vibration, and enhancing overall stability.

[0063] One of the four sets of stay cables 14, in the upright state, has its vertical plane parallel to the axial direction of the hinge pin 13, serving as the side to avoid when lowering the tower. When lowering the tower, this set of stay cables 14 is released, and its connection point is outside the tower's rotation trajectory, thus avoiding spatial interference with the tower.

[0064] VII. Installation and Downing for Inspection During the equipment installation phase, after the entire machine is laid flat on the ground and all parts are assembled and debugged, it is lifted to a 90° upright position by an external hydraulic synchronous lifting device around the hinge pin 13. The four sets of inclined cables 14 are then tensioned and locked, and the machine can be put into operation without the need for large hoisting equipment for high-altitude positioning.

[0065] During maintenance, first control the tower to retract to its lowest height (10m) and lock the blades; loosen the set of stay cables 14 parallel to the hinge pin 13. Figure 8 The tower is lowered to a 90° azimuth position, while the other three sets of stay cables 14 are simultaneously relaxed and unloaded. A hydraulic synchronous lifting device is used to control the lowering speed (not exceeding 0.5° / s), and the tower's tilt angle is monitored in real time. Using the hinge pin 13 as a fulcrum, the tower is smoothly lowered to a horizontal position, allowing all maintenance work on the nacelle, blades, and internal mechanisms to be completed on the ground, without any high-altitude operations. After maintenance, the tower is reversed and reset, and the stay cables 14 are tensioned to restore operation.

[0066] VIII. Performance Testing After 3,000 hours of continuous operation testing (including temperature cycling from -20℃ to +40℃ and simulated wind speed fluctuations from 0 to 25 m / s), the equipment in this embodiment exhibits smooth extension and retraction without jamming, dual-stage synchronization deviation ≤ ±1 mm, verticality error ≤ ±2 mm, and no slippage or shaking faults throughout the entire process.

[0067] In a typical low-wind-speed wind field with an average annual wind speed of 5.5 m / s, compared to a fixed-height tower (minimum storage height of 10 m) under the same wind field conditions, the annual power generation is increased by approximately 17.5%; under high-wind-speed conditions of 15 m / s, the overall wind load is reduced by approximately 28%; and the maintenance time is shortened from approximately 3 days / time for traditional fixed-tower maintenance (requiring large hoisting equipment) to 1 day / time, improving maintenance efficiency by approximately 60%. All performance characteristics meet design expectations.

[0068] Example 2: Based on the structural principle of Example 1, this example applies the invention to a wind turbine generator set with a rated power of 1.5MW. The parameters of each component are scaled up proportionally according to the load level. The maximum tower height is 70m and the minimum storage height is 20m (i.e., the minimum working height). It is suitable for Class III wind farms with an average annual wind speed of 5-7m / s.

[0069] Key parameters: Fixed cylinder 1: height 20m, bottom outer diameter Φ4200mm, top outer diameter Φ3600mm, wall thickness 28mm; First telescopic cylinder 2: stroke 17m, bottom outer diameter Φ3500mm, top outer diameter Φ3000mm, wall thickness 22mm; Second telescopic cylinder 3: stroke 34m, bottom outer diameter Φ2900mm, top outer diameter Φ2500mm, wall thickness 18mm. Maximum tower height = 20m + 17m + 34m = 71m ≈ 70m. The ratio of the second telescopic cylinder stroke to the electric cylinder stroke is 34m ÷ 17m = 2, satisfying a 1:2 stroke ratio.

[0070] The electric cylinder 4 has a rated thrust increased to 400kN, a stroke of 17m, and a rated speed of 0.12m / s; other parameters are the same as in Example 1. The traction rope 5 uses two parallel high-strength steel wire ropes (each with a diameter of 20mm, a structure of 6×36WS, and a tensile strength of 1770MPa). The pulley block 6 includes four fixed pulleys, arranged symmetrically in two groups. The locking teeth 10 are spaced 8cm apart. The stay cables 14 are configured in four groups, each consisting of three parallel steel strands. The remaining structural principles, control system, and adjustment methods are the same as in Example 1.

[0071] This embodiment demonstrates that the present invention can also achieve good adaptability at power levels of 1MW to 2MW, filling the power coverage gap between 200kW small power units and 3MW large power units, and verifying the feasibility of the present invention at intermediate power levels.

[0072] Example 3 is an optimization and upgrade based on Example 1, specifically designed for complex wind fields with frequent turbulence and gusts in mountainous terrain (turbulence intensity Iref ≥ 0.14, gust factor ≥ 1.4). Mountainous wind fields are characterized by severe wind speed fluctuations, frequent wind direction changes, and significant differences between high and low altitude wind conditions, requiring the tower to have higher response speed and control precision.

[0073] The electric cylinder 4 was replaced with a high-precision servo multi-stage electric cylinder, upgrading the repeatability to ±0.1mm. An acceleration feedforward control algorithm and a vibration suppression filter (notch filter, suppressing the first-order bending mode of the tower at frequencies of 1-5Hz) were added to cope with frequent gusts of wind in mountainous terrain. The spacing of the locking teeth 10 was increased to 5cm (approximately 160 locking points in total), improving the height locking accuracy to the 5cm level. The cylinder body adopts a lightweight hollow truss steel structure, reducing weight by approximately 25% while maintaining rigidity. The optimized structure can respond extremely quickly to wind speed fluctuations (response time ≤1.5s), precisely maintaining the optimal operating wind layer for the blades. Actual measurements show that compared to a tower of fixed height (minimum storage height 10m) under the same wind farm conditions, annual power generation increased by approximately 19.5%, and the standard deviation of the unit's power generation fluctuation decreased by approximately 35%.

[0074] Example 4: Based on the structural principle of Example 1, this example applies the invention to a large wind turbine with a rated power of 3MW. The parameters of each component are scaled up according to the load level. The maximum tower height is 120m and the minimum storage height is 30m (i.e., the minimum working height). It is suitable for Class II wind farms with an average annual wind speed of 6-8m / s.

[0075] Key parameters: Fixed cylinder 1: height 30m, bottom outer diameter Φ6000mm, top outer diameter Φ5000mm, wall thickness 40mm (material Q355E, suitable for -40℃ low temperature environment); First telescopic cylinder 2: stroke 30m, bottom outer diameter Φ4850mm, top outer diameter Φ4200mm, wall thickness 30mm; Second telescopic cylinder 3: stroke 60m, bottom outer diameter Φ4050mm, top outer diameter Φ3500mm, wall thickness 25mm. Maximum tower height = 30m + 30m + 60m = 120m. The ratio of the second telescopic cylinder stroke to the electric cylinder stroke is 60m ÷ 30m = 2, satisfying a 1:2 stroke ratio.

[0076] The rated thrust of the electric cylinder 4 is increased to 800kN, the stroke is 30m, and the rated speed is 0.08m / s (the speed is moderately reduced under high thrust conditions). The traction rope 5 uses four parallel high-strength steel wire ropes (each with a diameter of 24mm, a structure of 6×36WS, a tensile strength of 1960MPa, and a minimum breaking strength ≥320kN). The pulley block 6 adopts a double-row arrangement (four pulleys per row, for a total of eight fixed pulleys) to evenly distribute the load. The hinge pin 13 adopts a composite structure of a large slewing bearing and a pin (bearing diameter Φ800mm, load capacity ≥500t). The stay cables 14 are configured in six groups (uniformly arranged at 60° circumference), each group consisting of four parallel steel strands.

[0077] The tilting and maintenance function is optional and is mainly suitable for remote wind farms with limited installation conditions. For conventional wind farms with hoisting capabilities, traditional hoisting methods can also be used for maintenance. When tilting and maintenance is used, four synchronous hydraulic jacking devices are used in coordination (each with a rated lifting force of 200t and a synchronous control accuracy of ±3mm) to ensure a smooth and controllable tilting process. The remaining structural principles, control system, and adjustment methods are the same as in Example 1.

[0078] Simulation results show that, compared to a tower with a fixed height (minimum storage height of 30m), the annual power generation is expected to increase by about 13% to 18%, and the bending moment at the base of the tower is reduced by about 22% under extreme gust conditions.

[0079] This embodiment demonstrates that the present invention is not only applicable to small and medium-sized wind turbine units, but can also be adapted to large wind turbine units through reasonable selection and structural scaling, exhibiting good scalability.

[0080] The above description is merely a preferred embodiment of the present invention and is not intended to limit the invention. Any modifications, equivalent substitutions, and improvements made to the above embodiments within the scope of the inventive concept should be included within the protection scope of the present invention.

Claims

1. A telescopic tower with single cylinder drive rope and track system, characterized in that, include: Fixed cylinder (1); The first telescopic cylinder (2) is slidably sleeved inside the fixed cylinder (1); The second telescopic cylinder (3) is slidably sleeved inside the first telescopic cylinder (2); An electric cylinder (4) has its cylinder body fixed to the fixed cylinder (1) and its output rod connected to the first telescopic cylinder (2) for driving the first telescopic cylinder (2) to move axially. The linkage component includes a pulley block (6) installed on the first telescopic cylinder (2) and a traction rope (5) passing around the pulley block (6). The first end of the traction rope (5) is fixedly connected to the fixed cylinder (1), and the second end is fixedly connected to the second telescopic cylinder (3). In the lowest retracted state, the traction rope (5) is in a pre-tensioned state. When the electric cylinder (4) drives the first telescopic cylinder (2) to move, the traction rope (5) drives the second telescopic cylinder (3) to move in the same direction relative to the first telescopic cylinder (2), and the movement stroke of the second telescopic cylinder (3) is twice the movement stroke of the first telescopic cylinder (2).

2. A telescopic tower with single-cylinder driven rope linkage according to claim 1, characterized in that, It also includes a guiding mechanism, which includes a closed guide groove (8) disposed on the inner wall of the fixed cylinder (1) and a guide slider (9) disposed on the outer wall of the first telescopic cylinder (2). The guide slider (9) is embedded in the guide groove (8) to form a sliding fit. A sealing brush strip is installed at the opening of the closed guide groove (8) to prevent external impurities from entering the interior of the guide groove (8).

3. A telescopic tower with single-cylinder driven rope linkage according to claim 1, characterized in that, It also includes a locking mechanism, which is disposed between the fixed cylinder (1) and the first telescopic cylinder (2) for locking the position of the first telescopic cylinder (2) or the second telescopic cylinder (3) after it has moved into place; The locking mechanism includes a mechanical locking assembly, which includes a plurality of locking teeth (10) arranged along the axial direction of the first telescopic cylinder (2) and a locking claw (11) disposed on the fixed cylinder (1). The locking claw (11) can be engaged in the gap of the locking teeth (10) to achieve locking.

4. A telescopic tower with single-cylinder driven rope linkage according to claim 3, characterized in that, The electric cylinder (4) is a servo electric cylinder, and the locking mechanism also includes an electrical locking device integrated inside the electric cylinder (4), which is the brake of the servo electric cylinder.

5. A telescopic tower with single-cylinder driven rope linkage according to claim 1, characterized in that, The lower end of the fixed cylinder (1) is provided with a hinge pin (13) for hinge connection with the foundation, so that the telescopic tower can rotate around the hinge pin (13) between the upright state and the flat state. It also includes multiple sets of stay cables (14), one end of which is connected to the fixed cylinder (1) and the other end is used to anchor to the foundation; wherein at least one set of stay cables (14) is arranged in a direction parallel to the axis of the hinge pin (13) so that the set of stay cables (14) can be released when the tower is lowered to prevent motion interference.

6. A telescopic tower with single-cylinder driven rope linkage according to any one of claims 1 to 5, characterized in that, It also includes a control system, which includes a wind speed and direction sensor (12) and a main control unit. The main control unit is connected to the wind speed and direction sensor (12) and the electric cylinder (4) respectively, and is used to control the extension and retraction of the electric cylinder (4) according to the wind speed data collected by the wind speed and direction sensor (12).

7. A method for adaptive wind condition control of a telescopic tower with a single electric cylinder driving a rope system, characterized in that, Includes the following steps: S1: Obtain real-time wind speed data through wind speed and direction sensors; S2: Based on the wind speed data, control the electric cylinder of the telescopic tower to work, and drive the first telescopic cylinder (2) and the second telescopic cylinder (3) to extend and retract synchronously via the linkage component to adjust the tower height, wherein the travel of the second telescopic cylinder (3) is twice the travel of the first telescopic cylinder (2). The cylinder body of the electric cylinder (4) is fixed to the fixed cylinder (1), and the output rod is connected to the first telescopic cylinder (2). The linkage component includes a pulley group (6) installed on the first telescopic cylinder (2) and a traction rope (5) passing around the pulley group (6). The first end of the traction rope (5) is fixedly connected to the fixed cylinder (1), and the second end is fixedly connected to the second telescopic cylinder (3).

8. The wind condition adaptive control method for a telescopic tower with single-cylinder driven rope linkage according to claim 7, characterized in that, Step S2 includes: When the wind speed data is lower than the preset first threshold, the electric cylinder (4) is controlled to extend, so that the tower is raised to the highest working height; When the wind speed data is higher than the preset second threshold, the electric cylinder (4) is controlled to retract, so that the tower is lowered to the minimum working height; When the wind speed data is between the first threshold and the second threshold, the extension and retraction of the electric cylinder (4) is dynamically adjusted by the PID control algorithm to keep the blade in the target height range. The target height range is the height range with the smallest wind speed fluctuation and the most stable wind direction. This range is determined by wind speed gradient measurement or historical wind data statistics.

9. The wind condition adaptive control method for a telescopic tower with single-cylinder driven rope linkage according to claim 7, characterized in that, The retractable tower also includes a locking mechanism; before controlling the electric cylinder to work, the method includes a step of controlling the locking mechanism to unlock; after the tower height is adjusted to the correct position, the method includes a step of controlling the locking mechanism to lock.

10. The wind condition adaptive control method for a telescopic tower with single-cylinder driven rope linkage according to claim 7, characterized in that, It also includes the procedure of laying it down for maintenance: The control tower is retracted to its lowest height; Locking the blades; Loosen a group of stay cables (14) whose arrangement direction is parallel to the axis of the hinge pin (13), and simultaneously loosen the remaining stay cables (14) to relieve the force. Using the hinge pin (13) as the fulcrum, lower the tower to a flat position on the ground. After the maintenance is completed, the tower is erected and reset, and the stay cables (14) are tensioned.

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