Bridge cable tensioning and adjusting device

Abstract

The application provides a bridge cable-stayed cable tensioning and adjusting device, and relates to the technical field of bridge cable-stayed cable tensioning construction equipment. The application provides a bridge cable-stayed cable tensioning and adjusting device, and relates to the technical field of bridge cable-stayed cable tensioning construction equipment. The application provides a bridge cable-stayed cable tensioning and adjusting device, and relates to the technical field of bridge cable-stayed cable tensioning construction equipment. The application provides a bridge cable-stayed cable tensioning and adjusting device, and relates to the technical field of bridge cable-stayed cable tensioning construction equipment. The application provides a bridge cable-stayed cable tensioning and adjusting device, and relates to the technical field of bridge cable-stayed cable tensioning construction equipment. The application provides a bridge cable-stayed cable tensioning and adjusting device, and relates to the technical field of bridge cable-stayed cable tensioning construction equipment. The application provides a bridge cable-stayed cable tensioning

Description

Technical Field

[0001] This invention relates to the field of bridge cable tensioning construction equipment, and more specifically, to a bridge cable tensioning and adjustment device. Background Technology

[0002] In the construction and maintenance of cable-stayed bridges, the tensioning of the stay cables is a key process for controlling the bridge's alignment and internal forces. As the bridge span continues to increase, the tonnage and length of the stay cables also increase, placing higher demands on the loading capacity, control precision, construction efficiency, and operational safety of the tensioning equipment. Traditional tensioning processes often rely on large hydraulic jack systems, which can provide sufficient jacking force. However, when facing high-altitude, narrow tower or beam end work spaces, their massive size and weight make installation and transportation extremely inconvenient. At the same time, because the cable body will twist and angularly deviate during the tensioning process, if it is not effectively handled, it will lead to uneven stress on the anchorages, resulting in local stress concentration, which seriously affects the safety and durability of the bridge structure.

[0003] Therefore, the industry urgently needs a new type of tensioning device that can adapt to narrow spaces and automatically handle cable posture deviations. Summary of the Invention

[0004] The present invention aims to solve the problems that existing bridge cable tensioning and adjustment devices cannot adapt to narrow spaces and cannot automatically handle cable posture deviations.

[0005] To solve the above problems, the present invention provides a bridge cable tensioning and adjustment device, comprising: The cylindrical body is a hollow cylindrical structure extending along the axial direction, and is composed of three detachably connected sections: a first cylindrical body, a second cylindrical body, and a third cylindrical body. A flexible pressure equalizing sleeve is disposed inside the front end of the cylinder and is used to wrap and correct the cable body of the stay cable. An adjustment component is disposed between the rear end face of the cylinder and the anchor plate, which allows the cylinder to swing omnidirectionally relative to the anchor plate to compensate for anchoring misalignment. A force-enhancing transmission assembly is disposed inside the middle and rear section of the cylinder, behind the flexible pressure equalizing jacket, and is used to convert rotational power into axial thrust and drive the stay cable anchor head. The flexible pressure equalizing sleeve and the force amplifying transmission assembly are arranged at intervals in the axial direction. The output end of the force amplifying transmission assembly is connected to the stay cable anchor head, and the stay cable anchor head is located between the flexible pressure equalizing sleeve and the force amplifying transmission assembly.

[0006] The present invention provides a bridge cable tensioning and adjustment device, which, compared with the prior art, has, but is not limited to, the following beneficial effects: 1. Modular design and easy maintenance By dividing the cylinder into three detachable sections—the first, second, and third cylinders—each functional module can be independently disassembled and assembled. During on-site construction, worn parts (such as transmission components or seals) can be quickly replaced without requiring overall hoisting and disassembly, significantly reducing maintenance difficulty and downtime, making it particularly suitable for high-altitude or narrow bridge-deck work environments. 2. Flexible pressure equalizing sleeve enables cable protection and automatic centering. The flexible pressure-equalizing jacket wrapping the cable body not only effectively transmits radial clamping force, but also adapts to the slight bending or cross-sectional unevenness of the cable body during tensioning, avoiding damage to the steel strands (such as scratches and extrusion deformation) caused by rigid clamping. At the same time, its pressure-equalizing characteristics ensure that the tension force is evenly distributed along the circumference of the cable body, reducing local stress concentration and extending the fatigue life of the stay cable; 3. Omnidirectional swing adjustment component to compensate for anchorage misalignment The alignment component between the rear end face and the anchor plate allows the cylinder to swing in all directions (like a ball joint or universal joint structure), automatically compensating for angular misalignment of the anchor points caused by tower construction errors, temperature deformation, or load effects. This avoids the additional bending moment caused by misalignment in traditional rigid connections, ensuring that the tension force direction is always consistent with the cable axis, thus improving tensioning accuracy and structural safety. 4. Differential screw force amplification transmission enables high-tonnage precision tensioning. The second cylinder employs a differential principle with varying pitches to convert the rotational power of the hydraulic motor into axial thrust, achieving a large reduction ratio and increased force within a limited cylinder length. Compared to ordinary screw or hydraulic cylinder direct-push methods, this structure can output a larger tonnage of tensile force and has a self-locking function. It does not require continuous pressure supply during the load holding and pressure maintenance phase, making it energy-saving and safe, and particularly suitable for tensioning ultra-long, large-diameter cable-stayed cables.

[0007] 5. Compact axial layout and independent workspace The flexible equalizing jacket and the force-enhancing transmission component are arranged at intervals to make the clamping area and the power area independent of each other, so as to avoid the vibration or heat of the transmission components from being transferred to the jacket and affecting the cable gripping force. At the same time, the stay cable anchor head is located between the two, which makes it easy to directly observe the anchor head position and tightening status, and facilitates the construction personnel to adjust the tensioning stroke in real time.

[0008] 6. Reduce the risks of working at heights and improve construction efficiency. With a high degree of overall structural integration, the hydraulic motor can be quickly connected to an external pump station for tensioning simply by installing it on the top interface. No additional large reaction frame or jacks are required. The alignment component and differential spiral structure significantly reduce the time for auxiliary centering and leveling of the pad, shortening the tensioning cycle of a single cable, reducing the frequency of high-altitude operations, and improving construction safety and economy.

[0009] 7. Highly adaptable, capable of covering various cable types and offset working conditions. By replacing the flexible equalizing jacket of different specifications or adjusting the swing angle of the deflection adjustment component, this device can adapt to various cable bodies such as smooth cable, epoxy coated cable, and parallel steel wire cable, and can work normally in environments with anchor plate installation angle deviations of ±3°~±5°, demonstrating strong versatility and engineering adaptability.

[0010] Furthermore, the adjustment assembly includes a concave spherical base and a convex spherical top cover, which together form a spherical pair to allow the cylinder to swing omnidirectionally relative to the anchor plate to compensate for anchoring misalignment.

[0011] Furthermore, the flexible pressure equalizing jacket is composed of an inner polyurethane elastic pad and an outer steel retainer. The retainer has 12 to 24 cylindrical rollers evenly distributed circumferentially, with the roller axis parallel to the cable axis. The inner surface of the inner polyurethane elastic pad is in direct contact with the cable surface.

[0012] Furthermore, the spherical mating surfaces of the spherical pair are precision ground and coated with molybdenum disulfide grease, and the spherical pair allows the cylinder to swing omnidirectionally within ±3° relative to the concave spherical base.

[0013] Furthermore, the connecting end faces of the first cylinder, the second cylinder, and the third cylinder are machined with a stop positioning structure, which consists of mutually cooperating bosses and grooves. Each cylinder is fastened by quick-release flange bolts and self-locking nuts evenly distributed along the circumference.

[0014] Furthermore, the second cylinder is provided with a fixed nut seat mounting part and a gear ring mounting part inside, wherein the fixed nut seat mounting part and the gear ring mounting part are arranged axially back and forth at intervals, and a fixed nut seat is provided on the fixed nut seat mounting part, and the inner wall of the second cylinder forms a transition area between the fixed nut seat mounting part and the gear ring mounting part.

[0015] Furthermore, the power amplification transmission assembly includes a hydraulic motor, a planetary gear set, and a differential screw pair. The differential screw pair consists of a screw shaft, a bearing nut, and a fixed nut seat. The internal thread of the bearing nut engages with the external thread of the screw shaft, and the external thread of the bearing nut engages with the internal thread of the fixed nut seat fixed to the inner wall of the second cylinder. The pitch difference between the internal and external threads is 0.5 mm to 2 mm.

[0016] Furthermore, the planetary gear set is matched according to the output torque of the hydraulic motor and the required input torque of the differential helical pair.

[0017] Furthermore, the first cylinder includes a cylinder body, which is a hollow cylindrical structure extending along the axial direction, having a front end face, a rear end face, an inner wall, and an outer wall. The inner wall of the cylinder body forms, from front to back along the axial direction, a front step hole for installing the flexible equalizing jacket, an anchor head receiving cavity, a thrust bearing receiving cavity, and a bearing nut guide section, and the above-mentioned cavities are connected in sequence.

[0018] Furthermore, hydraulic pipelines are provided inside the first cylinder, the second cylinder, and the third cylinder. The hydraulic pipelines are provided with planar sealing self-sealing oil circuit joints at the connecting flange end faces of each cylinder. The self-sealing oil circuit joints include a first joint body and a second joint body respectively provided on the mating end faces of two adjacent cylinders. The first joint body and / or the second joint body are provided with a one-way valve core and an elastic element inside. When the cylinders are mated, the first joint body and the second joint body abut against each other and push against each other, overcoming the force of the elastic element, opening the one-way valve core, and connecting the oil circuits on both sides. When the cylinder separates, the one-way valve core automatically resets under the action of the elastic element, closing the corresponding oil passage and achieving oil circuit self-sealing. Attached Figure Description

[0019] Figure 1 This is a first schematic diagram of the structure of the bridge cable tensioning and adjustment device according to an embodiment of the present invention; Figure 2 This is a schematic diagram of the bridge cable tensioning and adjustment device according to an embodiment of the present invention after removing the force-increasing transmission component; Figure 3 This is a schematic cross-sectional view of the second cylinder according to an embodiment of the present invention; Figure 4 This is a schematic cross-sectional view of the overall cylindrical structure according to an embodiment of the present invention; Figure 5 This is a schematic diagram of the structure of the power-boosting transmission component in an embodiment of the present invention; Figure 6 This is a schematic diagram of the bridge cable tensioning and adjustment device according to an embodiment of the present invention after removing the second cylinder.

[0020] Explanation of reference numerals in the attached figures: 1. Cylinder body; 10. First cylinder body; 11. Second cylinder body; 110. Fixed nut seat mounting part; 111. Gear ring mounting part; 12. Third cylinder body; 2. Planetary gear set; 3. Differential helical pair; 30. Helical shaft; 31. Bearing nut. Detailed Implementation

[0021] To make the objectives, technical solutions, and advantages of this application clearer, specific embodiments of this application are described clearly and completely below with reference to the accompanying drawings. It should be understood that the described embodiments are only a part of the embodiments of this application, and not all of them. All other embodiments obtained by those skilled in the art based on the embodiments described in this application without creative effort will fall within the scope of protection of this application.

[0022] Unless otherwise defined, all technical and scientific terms used in this application have the same meaning as commonly understood by one of ordinary skill in the art to which this application pertains; the terminology used in the specification of this application is for the purpose of describing specific embodiments only and is not intended to limit this application; the terms "comprising," "including," "having," "containing," "comprise," etc., in the specification, claims, and accompanying drawings of this application are open-ended terms, indicating that a method comprises one or more steps, or an apparatus comprises one or more elements, but do not exclude the inclusion of other steps or elements. The terms "first," "second," etc., in the specification, claims, or accompanying drawings of this application are used to distinguish different objects, not to describe a specific order or primary / secondary relationship. 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 with "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of this application, unless otherwise stated, "a plurality of" means two or more.

[0023] In the description of this application, it should be understood that the terms "upper", "lower", "left", "right", "front", "rear", 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 application 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 application.

[0024] Furthermore, in the attached diagram, the X-axis represents the vertical direction, that is, the front-to-back position, and the positive direction of the X-axis (that is, the direction the arrow points to) represents the front, and the negative direction of the X-axis (that is, the direction opposite to the positive direction of the X-axis) represents the back; in the attached diagram, the Y-axis represents the horizontal direction, that is, the left-to-right position, and the positive direction of the Y-axis (that is, the direction the arrow points to) represents the left, and the negative direction of the Y-axis (that is, the direction opposite to the positive direction of the Y-axis) represents the right; in the attached diagram, the Z-axis represents the vertical direction, that is, the up-to-down position, and the positive direction of the Z-axis (that is, the direction the arrow points to) represents the up, and the negative direction of the Z-axis (that is, the direction opposite to the positive direction of the Z-axis) represents the down.

[0025] It should also be noted that the aforementioned X-axis, Y-axis and Z-axis are only for the purpose of facilitating the description of this application and simplifying the description, and are not intended to indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this application.

[0026] In the description of this application, it should be noted that, unless otherwise expressly specified and limited, the terms "installation," "connection," "linking," and "attachment" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal communication between two components. Those skilled in the art can understand the specific meaning of the above terms in this application according to the specific circumstances.

[0027] In this application, the term "and / or" is merely a description of the relationship between related objects, indicating that three relationships can exist. For example, A and / or B can represent: A existing alone, A and B existing simultaneously, or B existing alone. Additionally, in this application, the character " / " generally indicates that the preceding and following related objects have an "or" relationship.

[0028] In the actual construction of bridge stay cables, especially for the tensioning of large tonnage stay cables, the commonly used methods are mainly as follows: Firstly, a large-tonnage through-hole hydraulic jack is used for direct tensioning. This solution is technically mature, using a hydraulic pump station to drive the piston rod of the jack to extend and directly push the anchor head to achieve tensioning. Its advantages lie in its relatively simple structure, direct loading capacity, and ability to meet large-tonnage requirements. However, its disadvantages are also very obvious: the equipment is bulky and heavy, making installation and disassembly difficult in confined spaces at high altitudes; the hydraulic system has the risk of leakage, leading to pressure fluctuations and making it difficult to achieve high-precision cable force maintenance and fine-tuning; and the jack itself does not have the ability to correct cable torsion and compensate for angular deviations, requiring additional complex guiding and correction fixtures. Secondly, multiple small-tonnage jacks are used for parallel synchronous tensioning. This scheme arranges multiple small-sized jacks around the circumference of the anchor head and supplies oil synchronously in order to provide sufficient combined force while reducing the size of individual components. Its advantage is that the weight of individual components is reduced, making it easier to handle and assemble manually. However, its disadvantage is that it has extremely high requirements for the hydraulic synchronous control system. If there are differences in the load, internal leakage or frictional resistance of each jack, it is very easy to cause the synchronization accuracy to exceed the tolerance, resulting in uneven load on the anchor head or even jamming. The debugging process is complicated and the reliability is low. In addition, this scheme also fails to solve the problems of cable torsion and anchorage misalignment. Thirdly, a mechanical screw and nut mechanism is used for tensioning. This method uses manual labor or an electric motor to drive one or more large-lead trapezoidal screws to rotate, which in turn drives the load-bearing nut to move linearly, thereby pushing the anchor head. Its advantages are that the mechanical structure has self-locking properties, which can maintain the cable force well, and the control is relatively simple. However, its disadvantages are that in order to obtain a large thrust, the lead of the screw is usually large, resulting in a small mechanical gain and requiring a very large input torque. This places high demands on the drive source and the physical strength of the operator. At the same time, a large lead means poor fine-tuning ability, making it difficult to accurately control the final cable force value, and the transmission efficiency is low and wear is severe. Therefore, there is an urgent need for a new type of tensioning device that can adapt to narrow spaces, balance large-tonnage loading and high-precision control, and automatically handle cable posture deviations.

[0029] See Figures 1-6 According to an embodiment of the present invention, a bridge cable tensioning and adjustment device includes a cylinder 1, which is a hollow cylindrical structure extending along the axial direction, and is formed by a first cylinder 10, a second cylinder 11 and a third cylinder 12 being detachably fixedly connected along the axial direction. A flexible pressure equalizing sleeve (not shown in the figure) is provided inside the front end of the cylinder 1. The flexible pressure equalizing sleeve is used to wrap and clamp the cable body of the cable and correct the radial position of the cable body. An adjustment component is provided between the rear end face of the cylinder 1 and the anchor plate. The adjustment component is used to allow the cylinder 1 to swing omnidirectionally relative to the anchor plate to compensate for the anchoring deviation. A force-amplifying transmission assembly is provided inside the middle and rear section of the cylinder 1 and behind the flexible pressure equalizing jacket. The force-amplifying transmission assembly is used to convert rotational power into axial thrust and drive the stay cable anchor head to move axially. The flexible pressure equalizing jacket and the force-amplifying transmission assembly are arranged at an axial distance. The output end of the force-amplifying transmission assembly is driven to the stay cable anchor head. The stay cable anchor head is located axially between the flexible pressure equalizing jacket and the force-amplifying transmission assembly.

[0030] In this embodiment, since the first cylinder 10, the second cylinder 11 and the third cylinder 12 are detachably connected, and the flexible pressure equalizing sleeve and the force-enhancing transmission assembly are arranged axially at intervals, each functional module is physically independent. When it is necessary to replace the worn force-enhancing transmission assembly or adjust the clamping specifications of the flexible pressure equalizing sleeve on site, only the corresponding cylinder section needs to be disassembled to complete the operation. There is no need to lift and remove the entire device from the cable body. Thus, the disassembly difficulty and reassembly alignment error in high-altitude operation environment are effectively reduced, and the construction and maintenance efficiency and operation safety are significantly improved.

[0031] Meanwhile, in actual working scenarios, the flexible pressure equalizing sleeve is directly wrapped around the outside of the cable body. During the tensioning process, it utilizes the pressure equalizing characteristics of the flexible material to uniformly transmit the radial clamping force to the outer circumference of the cable body. Compared with rigid clamping, this structure avoids surface damage to the steel strands (such as indentations, scratches, or coating peeling) caused by excessive local clamping force or slight bending of the cable body. At the same time, the uniform radial stress distribution can automatically correct the slight axial deviation of the cable body. Thus, it ensures the linear transmission of tension force along the cable body axis, effectively extends the fatigue service life of the cable, and improves the uniformity of the force on the cable body during the tensioning process.

[0032] Furthermore, the deflection adjustment component is disposed between the rear end face of the cylinder and the pre-embedded anchor plate. The omnidirectional swing freedom it provides (such as a spherical hinge pair) allows the cylinder axis to adaptively follow the actual cable axis direction. It is worth noting that, since this structure is relatively simple and there is no ambiguity or difficulty in understanding, this technical feature is clear and unambiguous to those skilled in the art. Furthermore, the stay cable anchor head is axially positioned between the flexible equalizing sleeve and the force-enhancing transmission assembly, with the output end of the force-enhancing transmission assembly directly connected to it. This arrangement ensures that the tension force transmission path is "force-enhancing transmission assembly → anchor head → cable body," while the flexible equalizing sleeve only performs radial positioning and correction functions and does not directly bear the axial tension force. This achieves functional separation of axial tension and radial clamping force, avoiding premature fatigue failure of the sleeve due to combined stress. Simultaneously, it minimizes and directly directs the force transmission path, reduces stress loss in intermediate connecting parts, and improves energy transfer efficiency.

[0033] To ensure that those skilled in the art can understand the working principle and related structure of the adjustment component in this embodiment, specifically, the adjustment component includes a concave spherical base and a convex spherical top cover, which together form a spherical pair to allow the cylinder 1 to swing omnidirectionally relative to the anchor plate to compensate for anchorage misalignment; when the tower construction error or temperature deformation causes the normal direction of the anchor plate to form an angle with the theoretical axis of the cable, the component can automatically compensate for the angular misalignment, ensuring that the axial thrust of the force-enhancing transmission component always coincides with the axis of the cable, thereby fundamentally eliminating the additional bending moment caused by misalignment in traditional rigid connections, avoiding lateral deformation of the cylinder, and improving the transmission accuracy of tension force and the overall structural safety.

[0034] In addition, the flexible pressure equalizing jacket is composed of an inner polyurethane elastic pad and an outer steel cage. The cage has 12 to 24 cylindrical rollers evenly distributed circumferentially, with the roller axis parallel to the cable axis. The inner surface of the inner polyurethane elastic pad is in direct contact with the cable surface. In this embodiment, the cylindrical rollers of the flexible pressure equalizing jacket are made of high carbon chromium bearing steel GCr15, and the cage is made of brass or engineering plastic.

[0035] In this embodiment, the flexible pressure equalizing clamp is inserted into the front end inner hole of the first cylinder 10, and its outer wall is in clearance fit or small interference fit with the inner wall of the first cylinder 10. The inner surface of the inner polyurethane elastic liner is in direct contact with the surface of the cable, providing uniform radial pressure.

[0036] In this embodiment, the spherical mating surfaces of the spherical pair are precision ground and coated with molybdenum disulfide grease, and the spherical pair allows the cylinder 1 to swing omnidirectionally within ±3° relative to the concave spherical base.

[0037] Specifically, at this time, the rear end face of the concave spherical base abuts against the anchor plate of the bridge structure. The front end face of the convex spherical top cover is connected to the rear end face of the first cylinder 10 by a plurality of high-strength reamed bolts distributed circumferentially. The purpose is that the spherical mating surface achieves a high surface morphology accuracy (e.g., surface roughness Ra≤0.4μm) through precision grinding, effectively increasing the actual contact area and reducing the contact stress per unit area. Based on this, the coated molybdenum disulfide grease has a layered hexagonal lattice structure, which easily generates a low-shear-strength transfer film along the sliding direction under heavy pressure. This can transform the boundary lubrication state into a mixed lubrication state or even an elastohydrodynamic lubrication state. The two work together to significantly reduce the static and dynamic friction coefficients of the spherical pair when it is omnidirectionally swinging under axial tension heavy load (usually hundreds of tons). The resulting technical effects are: ① Reduced adjustment resistance, ensuring that the cylinder can swing sensitively and smoothly with the change of the cable axis, avoiding the failure of misalignment compensation due to friction jamming; ② Significantly reduced wear rate of the spherical pair, preventing deviation in the tension direction due to increased gap caused by wear, and maintaining the centering accuracy within the ±3° swing range for a long time. Furthermore, during the tensioning of the stay cables, due to the slight elastic elongation of the cable body during the load-bearing phase or fluctuations in ambient temperature, high-frequency micro-amplitude relative motion (fretting wear condition) inevitably exists between the mating surfaces of the spherical pair. Molybdenum disulfide grease has excellent anti-fretting wear performance; its solid lubricating particles can fill the microscopic oil reservoirs after grinding, continuously providing a solid lubricating film under fretting conditions, effectively isolating the direct contact between the metal substrates of the mating surfaces. This avoids the dry friction and adhesive tearing caused by traditional grease being expelled from the contact area under heavy load compression, significantly inhibiting pitting and abrasive wear of the spherical pair, thereby extending the maintenance cycle of the alignment component and the service life of the overall device. The spherical joint allows the cylinder 1 to swing omnidirectionally within ±3° relative to the concave spherical base. This angle range covers the installation angle deviation of anchor plates in conventional cable tower construction (usually ±1.5° to ±2.5°) and the change in cable direction caused by temperature and load. When there is an angle between the actual cable axis and the theoretical axis of the cylinder, the adjustment component automatically makes the cylinder axis and the cable axis coincide through the adaptive rotation of the spherical joint. The resulting technical effects are: ① It ensures that the axial thrust output by the force-enhancing transmission component is always transmitted along the actual axis of the cable, eliminating the additional bending moment and lateral component caused by the deviation, and avoiding the cylinder and connecting parts from bearing bending stress in non-design directions; ② Within the ±3° omnidirectional swing range, the contact stress distribution of the mating surface is always within the allowable range of the material, and there will be no edge stress concentration or jamming due to excessive deviation, ensuring structural safety redundancy under extreme deviation conditions.

[0038] Optionally, see Figure 4 The first cylinder 10, the second cylinder 11 and the third cylinder 12 are connected at their end faces with a stop positioning structure. The stop positioning structure consists of a boss and a groove that fit together. Each cylinder is fastened by quick-release flange bolts and self-locking nuts that are evenly distributed along the circumference.

[0039] In this embodiment, to improve the coaxiality and transmission accuracy of the cylinders during assembly, a precision fit (such as H7 / f6 clearance fit) is used between the boss and the groove to form a stop pair. When the end faces of each cylinder are mated, the stop pair first performs forced centering and positioning of the adjacent cylinders in the radial direction, so that the inner bore axes of the three cylinders tend to coincide after assembly. Compared with the method of centering and connecting only by flange bolts, this stop positioning structure has the following significant advantages: ① The bolts only need to bear the axial tightening force and do not need to bear the radial shear positioning load, avoiding the axial offset caused by wear of the positioning surface during repeated disassembly and assembly; ② The stop mating surface has a large radial positioning contact area, which can effectively resist the radial vibration and impact load generated during tensioning, ensuring that the meshing axis of the screw and nut in the force-enhancing transmission assembly is always consistent with the axis of the cable, thereby ensuring the straightness of motion transmission and transmission accuracy. Furthermore, to enhance connection stiffness and bending resistance, the boss and groove of the stop positioning structure form a closed annular mating surface in the radial direction. When the cylinder is subjected to bending moment or eccentric load generated by the tension reaction force, this mating surface provides continuous support and constraint, effectively suppressing radial misalignment and angular deflection at the connection. Simultaneously, multiple flange bolts evenly distributed along the circumference apply uniform axial preload, generating sufficient normal pressure between the stop mating surfaces, thus forming a reliable friction connection pair. The synergistic effect of these two factors significantly increases the bending section modulus at the cylinder connection, making the overall bending stiffness approach or even equal to that of a monolithic cylinder structure. This effectively avoids stress concentration or local bending deformation caused by abrupt changes in stiffness at segmented connections, ensuring structural continuity along the tension force transmission path.

[0040] Furthermore, the quick-release flange bolts employ a long screw structure that allows for rapid engagement, coupled with self-locking nuts (such as nylon insert self-locking nuts or all-metal deformed thread self-locking nuts). During cylinder connection and disassembly, no special tensioner or heating device is required; a conventional wrench is sufficient for tightening. The resulting technical advantages are: ① In high-altitude work environments, operators can quickly assemble and disassemble the cylinder without complex alignment adjustments, significantly reducing downtime during equipment relocation or component replacement and improving construction efficiency; ② The self-locking nuts rely on the locking torque within the threaded pair or the radial clamping force generated by the non-circular deformed threads to achieve mechanical anti-loosening under high-frequency vibration and continuous heavy-load conditions during tensioning, effectively avoiding the risk of loosening due to vibration fatigue associated with traditional ordinary nuts and spring washers; ③ The large flange bearing surface of the flange bolts reduces the compressive stress acting on the cylinder end face, preventing end face deformation caused by localized crushing and protecting the precision of the stop mating surface.

[0041] Meanwhile, the bolts are evenly arranged along the flange circumference, ensuring that the axial preload applied to each connection point is consistent and that the contact pressure distribution is uniform throughout the entire circumference of the mating surface. This avoids, on the one hand, the jamming of the force-amplifying transmission component caused by unilateral deformation of the cylinder due to excessive tightness, and on the other hand, ensures a tight seal between adjacent cylinder end faces, preventing external rainwater, dust, and other impurities from entering the cylinder and protecting the normal operating environment of the flexible pressure-equalizing jacket and the force-amplifying transmission component.

[0042] See Figures 2-4 The second cylindrical body 11 is provided with a fixed nut seat mounting part 110 and a gear ring mounting part 111 inside. The fixed nut seat mounting part 110 and the gear ring mounting part 111 are arranged axially at intervals, and a fixed nut seat is provided on the fixed nut seat mounting part 110. The inner wall of the second cylindrical body 11 forms a transition area between the fixed nut seat mounting part 110 and the gear ring mounting part 111.

[0043] Based on the above structural features, its technical effects are derived as follows: (1) Optimization of force flow transmission path and stress interference suppression effect based on "axial spacing arrangement" The fixed nut seat mounting part 110 is used to bear the axial reaction force transmitted by the fixed nut seat during tensioning. This is the main load-bearing area of ​​the second cylinder 11, and its force direction is opposite to the tensioning force direction. The gear ring mounting part 111 is used to install the transmission gear ring. This part mainly bears the circumferential driving torque and the corresponding radial component force generated by the gear ring meshing. The two are arranged axially at intervals, so that the two loads of different natures and directions act on different axial sections of the cylinder respectively. Compared with the scheme of arranging the two on the same axial section, this interval arrangement has the following significant advantages: ① It avoids the superposition and coupling of axial reaction force and circumferential driving force on the same cylinder section, preventing local yielding or fatigue cracking of the cylinder due to composite stress concentration; ② The axial reaction force and circumferential driving force each form an independent force flow transmission path along the cylinder wall thickness direction. The two force flow paths naturally attenuate in the transition area and merge into the overall load-bearing system of the cylinder. The force line distribution is clear and continuous, without abrupt changes or cross interference, thereby improving the stress rationality and load-bearing efficiency of the cylinder structure.

[0044] (2) The effect of gradual stress gradient transition and structural fatigue resistance based on the "transition region" The transition region between the fixed nut seat mounting part 110 and the gear ring mounting part 111 is a smooth inner wall section without steps or sharp corners. This region achieves a natural connection in wall thickness or cross-sectional shape between the two mounting parts geometrically, avoiding stress concentration caused by abrupt changes in cross-section. During tensioning operations, the high-pressure axial stress borne by the fixed nut seat mounting part 110 is gradually attenuated and transferred to the gear ring mounting part 111 and the subsequent cylinder through this transition region. The resulting technical effects are: ① A gentle stress gradient distribution is formed along the axial direction of the cylinder, making the stress level of each cross-section of the cylinder tend to be uniform, avoiding a sudden increase in stress at a certain cross-section that exceeds the material fatigue limit; ② Under alternating tension loads (multiple tensioning, holding, and unloading cycles of the stay cable), this transition region effectively reduces the stress amplitude concentration factor, significantly improves the fatigue life of the cylinder, and ensures the reliability of the device throughout the entire life cycle of the bridge.

[0045] (3) Thermal deformation isolation and transmission accuracy maintenance effect based on "axial spacing arrangement" During the tensioning operation, the threaded mating surfaces of the fixed nut seat and the second cylinder 11 generate a large amount of heat due to friction, causing the cylinder temperature in the area of ​​the fixed nut seat mounting part 110 to rise. Simultaneously, the area of ​​the gear ring mounting part 111 also experiences a temperature rise due to the gear ring's meshing transmission. The two are arranged axially spaced and separated by a transition region, ensuring that the two heat sources are spatially distant. This transition region has a certain axial length, and its cylinder material has a thermal conduction damping effect, effectively slowing down the rate of heat transfer along the cylinder's axial direction. This avoids a uniform temperature rise between the fixed nut seat mounting part 110 and the gear ring mounting part 111 due to rapid heat transfer, preventing unidirectional thermal expansion due to temperature convergence, which could alter the axial relative position between the fixed nut seat and the gear ring. This structural feature effectively ensures that the meshing clearance and transmission accuracy of the force-enhancing transmission assembly are not affected by thermal deformation, ensuring precise control of the tension force under continuous operation conditions.

[0046] (4) The ease of assembly and maintenance based on the "separation of the fixed nut seat mounting part and the gear ring mounting part" The fixed nut seat mounting part 110 and the gear ring mounting part 111 are arranged axially spaced, allowing the fixed nut seat and the transmission gear ring to have their own independent assembly space and operating window inside the cylinder. During assembly, the fixed nut seat can be positioned and fastened independently on the nut seat mounting part 110 first, and then the gear ring can be installed and adjusted independently on the gear ring mounting part 111, without interference between the two. During maintenance, if it is necessary to replace a worn fixed nut seat or repair the gear ring, only the connecting parts of the corresponding mounting parts need to be disconnected for individual replacement, without the need to disassemble both at the same time. This reduces the assembly difficulty of the complex transmission system inside the cylinder and improves the convenience and efficiency of on-site maintenance operations.

[0047] In this embodiment, the force-enhancing transmission assembly includes a hydraulic motor, a planetary gear set 2, and a differential screw pair 3. The differential screw pair 3 consists of a screw shaft 30, a bearing nut 31, and a fixed nut seat. The internal thread of the bearing nut 31 engages with the external thread of the screw shaft 30, and the external thread of the bearing nut 31 engages with the internal thread of the fixed nut seat fixed to the inner wall of the second cylinder 11. The pitch difference between the internal and external threads is 0.5 mm to 2 mm.

[0048] Based on the technical features of the aforementioned power-enhancing transmission component, its technical effects are derived as follows: (1) Differential force amplification principle based on "small pitch difference" and ultra-large thrust output effect The differential screw pair 3 adopts a double-thread differential transmission method. When the hydraulic motor drives the screw shaft 30 to rotate via the planetary gear set 2, the bearing nut 31 tends to move axially under the drive of the external thread of the screw shaft 30. At the same time, since its external thread meshes with the internal thread of the fixed nut seat, the bearing nut 31 is forced to feed axially along the internal thread of the fixed nut seat. Due to the different pitches of the two pairs of screw pairs, the difference between the axial displacement velocity of the bearing nut 31 relative to the fixed nut seat and its axial displacement velocity relative to the screw shaft 30 is equal to the feed amount corresponding to the pitch difference. Its kinematic relationship is: when the screw shaft 30 rotates one revolution, the actual axial displacement of the bearing nut 31 relative to the fixed nut seat is equal to the pitch difference ΔP (when P1>P2, the bearing nut moves forward P1 relative to the screw shaft, while the fixed nut seat forces the bearing nut to move forward P2 relative to itself, and the net displacement is P1-P2). The pitch difference is set to 0.5mm to 2mm, which is significantly smaller than the nominal pitch of each of the two threaded pairs (typically in the range of 8mm to 20mm). Therefore, a very large motion reduction ratio can be obtained using a small displacement input, with a reduction ratio i = P1 / (P1-P2) reaching tens to hundreds of times. According to the principles of energy conservation and virtual work, under ideal conditions where frictional losses are ignored, the axial output force is proportional to the input driving torque. The resulting technical effect is that the hydraulic motor can drive the helical shaft 30 to output tens or even hundreds of tons of axial thrust with a small torque input, pushing the stay cable anchor head to achieve tensioning operations, effectively solving the contradiction between the ultra-large tonnage thrust required for bridge stay cable tensioning and the limited hydraulic power of the bridge deck.

[0049] (2) Effect of slow precision feed and precise tension control based on "0.5mm~2mm pitch difference" The differential screw pair 3, while reducing speed and increasing force, converts the large-angle rotational motion of the input into a small axial displacement at the output end. Taking a pitch difference ΔP = 1mm as an example, when the screw shaft 30 rotates once, the nut 31 and the anchor head of the cable driven by it only move axially by 1mm. If the hydraulic motor is further reduced by the planetary gear set 2 (for example, reduction ratio i2 = 5), the anchor head will only move 1mm after the motor rotates 5 times, which is equivalent to the anchor head moving only 0.2mm for every 1 rotation of the motor. The resulting technical effects are: ① The operator can achieve continuous, micron-level precision adjustment of the cable tension by controlling the rotation angle of the hydraulic motor, avoiding cable force overshoot or oscillation caused by pressure fluctuations in traditional hydraulic jacks; ② In the fine-tuning stage after the cable is tensioned to the design value (such as when the cable force deviation is within ±1%), the differential micro-feed characteristic can be used for fine compensation to ensure that the cable force uniformity among multiple cables meets the design requirements.

[0050] (3) Leak-free load holding and pressure maintenance effect based on the "differential screw pair self-locking condition" As a mechanical transmission mechanism, the differential screw pair 3 has a helix angle design that satisfies the self-locking condition, i.e., the equivalent friction angle is greater than the helix angle. After the tension reaches the set value and the hydraulic motor drive stops, the reverse tension generated by the elastic recovery of the stay cable acts on the bearing nut 31. This reverse thrust is converted into rotational torque through the threaded pair. Since the equivalent friction angle of the threaded pair is greater than the helix angle, this reverse rotational torque is insufficient to overcome the static friction between the threaded pairs. Therefore, a self-locking mechanism is formed between the screw shaft 30 and the bearing nut 31, and the position of the bearing nut 31 relative to the fixed nut seat is mechanically locked. The resulting technical effects are: ① During the load-bearing stage, there is no need for continuous pressure supply from the hydraulic system, eliminating the cable force attenuation problem caused by aging seals and internal oil leakage in traditional hydraulic cylinders, achieving true long-term stable pressure maintenance; ② The energy consumption of the hydraulic pump station required for continuous pressure supply is eliminated, reducing construction energy consumption. At the same time, it can still reliably maintain tension in the event of unexpected power failure or hydraulic system failure, significantly improving operational safety redundancy.

[0051] (4) The effect of secondary force amplification and compact layout based on "planetary gear set and differential screw pair in series" The primary rotational power output by the hydraulic motor first undergoes a first-stage reduction and torque amplification via the planetary gear set 2, and then is input to the differential screw pair 3 for a second-stage reduction and force amplification. The planetary gear set 2 features a compact structure, high load-bearing capacity, and high transmission efficiency (up to 97%~98% per stage), enabling it to achieve a large primary reduction ratio (typically 3~10) within the limited radial space of the cylinder. The differential screw pair 3, connected in series thereafter, further achieves a secondary reduction of tens of times. Together, they form a second-stage force amplification transmission chain with a "large reduction ratio and high power density". The resulting technical benefits are: ① Compared to a single-stage force amplification scheme relying solely on differential helical pairs, the tandem planetary gear set can achieve flexible adjustment of the total reduction ratio through planetary compensation within the range of the differential helical pair pitch difference (0.5mm~2mm) without excessively reducing the pitch difference (too small a pitch difference will lead to machining difficulties and the risk of self-locking failure), thus reducing the machining difficulty of precision threaded pairs; ② The two-stage force amplification mechanism is coaxially nested inside the cylinder, resulting in a compact overall axial length, avoiding the problem of the overall size of the device being too large to be arranged in the narrow space of the bridge deck due to the use of multi-stage hydraulic cylinders or external gearboxes.

[0052] (5) Optimization effect of axial force balance and cylinder bearing capacity based on "coordinated internal and external thread feed" During the operation of the differential screw pair 3, the bearing nut 31 is simultaneously subjected to the driving force of the screw shaft 30 (transmitted through the internal thread) and the constraint force of the fixed nut seat (transmitted through the external thread). The two forces are equal in magnitude and opposite in direction, and are balanced within the bearing nut 31. The fixed nut seat directly transmits the axial reaction force transmitted by the bearing nut 31 to the entire cylinder 1 via the fixed nut seat mounting part 110 of the second cylinder 11. The resulting technical effects are: ① As an intermediate force-bearing element, the bearing nut 31 bears loads simultaneously through its internal and external threads, and the force per unit area is less than that of the single thread scheme, which improves the contact stress distribution of the thread pair and reduces the risk of shear and bending fatigue of the thread teeth; ② The axial tension reaction force is directly transmitted to the cylinder wall through the fixed nut seat, and the force flow path is short and direct, avoiding the additional bending moment and assembly error accumulation caused by transmission through other intermediate connecting parts.

[0053] It is worth noting that the planetary gear set 2 is matched according to the output torque of the hydraulic motor and the input torque required by the differential helical pair 3. In this embodiment, an NGW type planetary gear set with a speed ratio of 3:1 to 5:1 is selected, and the materials of the helical shaft 30 and the bearing nut 31 of the differential helical pair 3 are high-strength alloy steel.

[0054] In this embodiment, the first cylinder 10 includes a cylinder body, which is a hollow cylindrical structure extending along the axial direction, having a front end face, a rear end face, an inner wall and an outer wall. The inner wall of the cylinder body forms, from front to back along the axial direction, a front step hole 101 for installing a flexible pressure equalizing jacket, an anchor head receiving cavity, a thrust bearing receiving cavity and a bearing nut guide section 100, and the above-mentioned cavities are connected in sequence.

[0055] The front stepped hole 101 is used to install a flexible equalizing sleeve, which undertakes the radial clamping and positioning functions of the cable body; the anchor head receiving cavity is used to accommodate the stay cable anchor head and provide axial movement space for the anchor head; the thrust bearing receiving cavity is used to install the thrust bearing and bear the axial load during the tensioning process; the bearing nut guide section 100 is used to provide a sliding mating surface for guidance and constrain the axial movement direction of the bearing nut. The above-mentioned cavities are arranged in sequence along the axial direction, so that the clamping function, anchor head receiving function, axial bearing function and guiding function are spatially independent and do not overlap with each other; The resulting technical effects are: ① The load types borne by each functional area are clear and singular. The front step hole mainly bears the radial clamping force, the thrust bearing cavity mainly bears the axial pressure, and the guide section mainly bears the radial constraint force, avoiding the composite stress state caused by the superposition of multiple loads on the same cylinder section, and simplifying the strength verification and wall thickness design of each section of the cylinder; ② The processing accuracy requirements of each functional area can be set independently according to their respective functions. For example, the guide section requires high precision, and the anchor head receiving cavity can be appropriately relaxed, reducing the overall processing cost.

[0056] Secondly, the stepped end face of each cavity provides an axial positioning reference for the corresponding component, avoiding the cumulative coaxiality error caused by machining multiple independent parts separately and then assembling them. This ensures that the clamping center of the flexible pressure equalizing jacket, the movement axis of the anchor head, the bearing center of the thrust bearing, and the guide axis of the bearing nut are highly coincident. At the same time, when replacing worn parts later, operators can push out the old parts and push in the new parts along the axial direction without disassembling the entire cylinder, simplifying the on-site maintenance process.

[0057] In this embodiment, hydraulic pipelines are provided inside the first cylinder 10, the second cylinder 11, and the third cylinder 12. The hydraulic pipelines have planar sealing self-sealing oil circuit connectors at the connecting flange ends of each cylinder. Each self-sealing oil circuit connector includes a first connector body and a second connector body respectively disposed on the mating end faces of two adjacent cylinders. The first connector body and / or the second connector body are internally provided with a one-way valve core and an elastic element. When the cylinders are mated, the first connector body and the second connector body abut against each other and push against each other, overcoming the force of the elastic element and opening the one-way valve core, thus connecting the oil circuits on both sides. When the cylinders are separated, the one-way valve core automatically resets under the action of the elastic element, closing the corresponding oil circuit passage, achieving self-sealing of the oil circuit.

[0058] Specifically, the first and second connector bodies are respectively embedded in the mating flange end faces of adjacent cylinders, and their mating end faces are precision-ground flat sealing structures. When the two cylinders are fastened with flange bolts, the mating end faces fit together, and the front ends of the first and second connector bodies abut against each other, generating axial pushing force. This pushing force overcomes the preload of the built-in elastic element (such as a compression spring), pushing the one-way valve core axially backward, causing the valve core to disengage from the valve seat, and opening the oil passage. The resulting technical effects are: ① While the cylinders are mechanically connected, the hydraulic pipeline automatically completes the oil circuit connection, eliminating the need for additional oil pipe connector insertion and removal operations, achieving one-step mechanical and hydraulic connection, and significantly shortening on-site installation time; ② The mating fit of the flat sealing end faces ensures no external leakage when the oil circuit is connected, and the oil circuits on both sides form a smooth hydraulic passage the moment the valve core opens, ensuring that the hydraulic oil can reach the hydraulic motor and each actuator simultaneously, avoiding the problem of asynchronous operation of actuators due to delayed oil supply. In addition, when disassembly is required for maintenance or component replacement, after the operator loosens the flange bolts, the adjacent cylinders separate axially. During the separation process, the mutual contact force between the first and second connectors gradually decreases until it disappears. At this time, the built-in elastic element (such as a compression spring) uses its pre-stored elastic potential energy to drive the one-way valve core to move towards the valve seat until the sealing surface of the valve core is tightly fitted with the valve seat, thus achieving self-closure of the oil passage. The resulting technical effects are: ① There is no need to pre-emptively drain the hydraulic oil inside the cylinder during disassembly. After the one-way valve core self-seales, the oil passages in each cylinder section remain independently closed, and the hydraulic oil is locked inside each cylinder, preventing it from flowing out from the disconnected joint, thus eliminating environmental pollution and safety hazards caused by on-site oil leakage; ② There is no need to perform pipeline venting or oil replenishment operations during reassembly, because the oil in each cylinder section remains full in the self-sealing state. After docking, the oil passages are connected, and the hydraulic transmission function can be restored immediately, avoiding the cumbersome process of repeated venting required by traditional quick-connect couplings due to oil loss during disassembly and assembly. Meanwhile, the mating surfaces of the first and second connector bodies adopt a planar sealing form. The sealing surfaces are precision ground, achieving a surface roughness of Ra≤0.8μm and a flatness within 0.01mm. When adjacent cylinders are mated, the tightening force of the flange bolts ensures a tight fit between the two planar sealing surfaces, forming an initial metal-to-metal contact sealing barrier. Simultaneously, the microscopic unevenness between the sealing surfaces is sealed by residual hydraulic oil forming an oil film. The resulting technical effects are: ① The planar sealing structure can withstand the working pressure of the hydraulic system (typically up to 25MPa~35MPa) without external leakage, and its sealing performance increases with increasing system pressure (the higher the pressure, the tighter the sealing surface fits), exhibiting self-tightening sealing characteristics; ② Compared to O-ring radial sealing or end-face sealing, the planar seal eliminates the risk of sealing ring aging, twisting, or extrusion failure. It maintains reliable sealing performance even under repeated disassembly and reassembly (up to hundreds of times within its design life), significantly improving the reliability of the device.

[0059] More notably, because each cylinder section has its own independent hydraulic pipeline with self-sealing oil line connectors at both ends, each cylinder section forms an independent closed oil circuit unit when disassembled. The resulting technical advantages are: ① During the factory production and commissioning phase, each cylinder section can undergo hydraulic pipeline pressure tests and leak detection separately, allowing for quality inspection without assembling the entire machine, reducing commissioning difficulty and rework costs; ② In field use, if a hydraulic component in a cylinder section (such as a hydraulic motor installed in the third cylinder) malfunctions, that cylinder section can be disassembled for repair or replacement, while the hydraulic pipelines of other cylinder sections remain sealed through self-sealing connectors, eliminating the need for overall pressure relief or oil draining, thus reducing the impact of maintenance on the overall hydraulic system.

[0060] Furthermore, the one-way valve core and its seat are built into the cavities of the first and second connector bodies, and are not directly exposed to the external environment. When the cylinders are separated, the valve core resets and closes the oil circuit, while simultaneously isolating the connector cavity from the outside. When the cylinders are joined, the front ends of the two connector bodies form a sealed contact before the valve core opens, preventing external air or impurities from entering the oil circuit. The resulting technical effects are: ① Effectively prevents dust, rainwater, concrete slurry, and other contaminants from the bridge construction site from entering the hydraulic system during disassembly and assembly, avoiding hydraulic valve jamming, hydraulic motor wear, or filter clogging caused by contaminants, thus extending the service life of hydraulic components; ② Driven by the elastic element, the valve core generates a slight relative movement with the valve seat each time it resets. This movement has a self-cleaning effect, capable of shearing or squeezing out tiny particles on the valve seat sealing surface, preventing long-term deposition of impurities on the sealing surface that could lead to sealing failure.

[0061] While the present invention has been disclosed above, its scope of protection is not limited thereto. Those skilled in the art can make various changes and modifications without departing from the spirit and scope of the present invention, and all such changes and modifications will fall within the scope of protection of the present invention.

Claims

1. A bridge cable tensioning and adjustment device, characterized in that, include: The cylindrical body (1) is a hollow cylindrical structure extending along the axial direction, and is composed of three detachably connected sections: a first cylindrical body (10), a second cylindrical body (11), and a third cylindrical body (12). A flexible pressure equalizing sleeve is provided inside the front end of the cylinder (1) to wrap and correct the cable body of the stay cable; The adjustment component is disposed between the rear end face of the cylinder (1) and the anchor plate, and is used to allow the cylinder (1) to swing omnidirectionally relative to the anchor plate to compensate for the anchoring deviation. The force-enhancing transmission assembly is located inside the middle and rear section of the cylinder (1), behind the flexible pressure equalization jacket, and is used to convert rotational power into axial thrust and drive the cable anchor head. The flexible pressure equalizing sleeve and the force amplifying transmission assembly are arranged at intervals in the axial direction. The output end of the force amplifying transmission assembly is connected to the stay cable anchor head, and the stay cable anchor head is located between the flexible pressure equalizing sleeve and the force amplifying transmission assembly.

2. The bridge cable tensioning and adjustment device according to claim 1, characterized in that, The adjustment assembly includes a concave spherical base and a convex spherical top cover, which together form a spherical pair to allow the cylinder (1) to swing omnidirectionally relative to the anchor plate to compensate for anchoring misalignment.

3. The bridge cable tensioning and adjustment device according to claim 1, characterized in that, The flexible pressure equalizing jacket consists of an inner polyurethane elastic pad and an outer steel retainer. The retainer has 12 to 24 cylindrical rollers evenly distributed circumferentially, with the roller axes parallel to the cable axis. The inner surface of the inner polyurethane elastic pad is in direct contact with the cable surface.

4. The bridge cable tensioning and adjustment device according to claim 2, characterized in that, The spherical mating surfaces of the spherical pair are precision ground and coated with molybdenum disulfide grease. The spherical pair allows the cylinder (1) to swing in all directions within ±3° relative to the concave spherical base.

5. The bridge cable tensioning and adjustment device according to claim 1, characterized in that, The first cylinder (10), the second cylinder (11) and the third cylinder (12) are connected by a stop positioning structure. The stop positioning structure consists of a boss and a groove that fit together. Each cylinder is fastened by quick-release flange bolts and self-locking nuts that are evenly distributed along the circumference.

6. The bridge cable tensioning and adjustment device according to claim 1, characterized in that, The second cylindrical body (11) is provided with a fixed nut seat mounting part (110) and a gear ring mounting part (111) inside. The fixed nut seat mounting part (110) and the gear ring mounting part (111) are arranged axially back and forth at intervals, and a fixed nut seat is provided on the fixed nut seat mounting part (110). The inner wall of the second cylindrical body (11) forms a transition area between the fixed nut seat mounting part (110) and the gear ring mounting part (111).

7. A bridge cable tensioning and adjustment device according to claim 6, characterized in that, The power amplification transmission assembly includes a hydraulic motor, a planetary gear set (2), and a differential screw pair (3). The differential screw pair (3) consists of a screw shaft (30), a bearing nut (31), and a fixed nut seat. The internal thread of the bearing nut (31) engages with the external thread of the screw shaft (30), and the external thread of the bearing nut (31) engages with the internal thread of the fixed nut seat fixed to the inner wall of the second cylinder (11). The pitch difference between the internal and external threads is 0.5 mm to 2 mm.

8. A bridge cable tensioning and adjustment device according to claim 7, characterized in that, The planetary gear set (2) is matched according to the output torque of the hydraulic motor and the required input torque of the differential helical pair (3).

9. A bridge cable tensioning and adjustment device according to any one of claims 5-8, characterized in that, The first cylinder (10) includes a cylinder body, which is a hollow cylindrical structure extending along the axial direction, having a front end face, a rear end face, an inner wall and an outer wall. The inner wall of the cylinder body forms a front step hole (101) for installing a flexible pressure equalizing jacket, an anchor head receiving cavity, a thrust bearing receiving cavity and a bearing nut guide section (100) in sequence from front to back along the axial direction. The above-mentioned cavities are connected in sequence.

10. A bridge cable tensioning and adjustment device according to claim 9, characterized in that, Hydraulic pipelines are provided inside the first cylinder (10), the second cylinder (11), and the third cylinder (12). The hydraulic pipelines are provided with planar sealing self-sealing oil circuit joints at the connecting flange end faces of each cylinder. The self-sealing oil circuit joints include a first joint body and a second joint body respectively provided on the mating end faces of two adjacent cylinders. The first joint body and / or the second joint body are provided with a one-way valve core and an elastic element inside. When the cylinders are mated, the first joint body and the second joint body abut against each other and push against each other, overcoming the force of the elastic element, and opening the one-way valve core to connect the oil circuits on both sides. When the cylinders are separated, the one-way valve core automatically resets under the action of the elastic element, closing the corresponding oil circuit channel and realizing the self-sealing of the oil circuit.

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