A partially self-centering frictional damping double-sleeve device and device parameter calculation method

Abstract

The present application relates to the technical field of civil engineering energy dissipation and shock absorption, and particularly relates to a partially self-resetting frictional damping double-sleeve device and a device parameter calculation method. Through the mutual cooperation of the inner sleeve and the outer sleeve, basic structural support is provided for the entire device. The planar frictional damper and the recoverable slope frictional damper are innovatively combined and distributed in a cross shape around the sleeve, and can respond to the axial deformation of the inner sleeve in all directions. Under the action of an earthquake or accidental gravity load, the recoverable slope frictional damper and the planar frictional damper work cooperatively to consume the potential energy of the axial deformation of the inner sleeve, effectively solving the buckling problem of the tensile string truss structure. At the same time, the energy dissipation capacity compensates for the defect of insufficient energy dissipation of the structure, and the improved stiffness also makes the structure more stable. Moreover, they can also generate a reverse force to reset the inner sleeve, significantly enhancing the recoverable performance of the structure under special loads, and guaranteeing the safety and reusability of the tensile string truss structure under extreme conditions.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of civil engineering energy dissipation and shock absorption, in particular to a partially self-centering frictional damping double-sleeve device and a device parameter calculation method. BACKGROUND

[0002] In today's field of construction engineering, the truss string structure has become the preferred structure form for large space important public buildings such as exhibition centers and airports, with its light and beautiful shape, reasonable and efficient stress characteristics, and outstanding span advantage. This structure design not only realizes efficient use of space, but also effectively saves the amount of steel structure, while having strong structural stability, combining the dual values of aesthetics and practicality. For this reason, the truss string structure has been widely applied and vigorously promoted in modern construction engineering.

[0003] However, with the continuous expansion of the application range of the structure, structure collapse accidents also occur from time to time, bringing severe challenges to the safety of construction engineering. Especially for the truss string structure, its redundancy is relatively low, and the cable as a key component is self-evident. Once the cable or other key components fail, the load transfer path of the structure will change greatly and be difficult to predict, which may cause a continuous collapse accident. The root cause of this is that the sleeve component in the truss string structure is prone to buckling under compression, and once buckling occurs, its carrying capacity will be significantly reduced, thus causing a series of serious collapse consequences.

[0004] In order to further explore the collapse mechanism of prestressed large-span truss string structures, many scholars have devoted themselves to related research and proposed a series of research methods and models with their own characteristics. And the current research results clearly show that the use of additional sleeve reinforcement measures on the outside of the truss string structure, the reasonable arrangement of energy dissipation dampers to improve the energy dissipation capacity of the structure, or the clever arrangement of steel strands to increase the stiffness after compression yield can significantly improve the anti-collapse ability of the truss string structure and effectively reduce the collapse displacement of the structure, thus achieving precise and effective control of the collapse degree of the structure.

[0005] Traditional structural forms, such as flexural frames or buckling-restrained brace frames, mainly rely on joints or supports to achieve energy dissipation function. However, once the key lateral force resisting member joint of such structures is damaged, repair work will face great difficulties, and the repair cost is usually very high, even exceeding the construction cost of the structure. The joints of the truss string structure usually use welding technology, so under the action of earthquakes, they also face the problems of repair difficulty and high cost.

[0006] In this context, self-centering structures, i.e. structures that can restore functionality, have emerged and been widely developed and applied. Self-centering structures have many significant advantages, including strong seismic resistance, ease of repair, and economic flexibility. However, due to the relatively low energy dissipation of self-centering structures, in order to further improve the energy dissipation capacity of the structure, scholars have conducted in-depth research and practical exploration, and through the innovative method of reducing the proportion of self-centering dampers and energy dissipation devices, successfully developed a partial self-centering energy dissipation device. The actual application results show that under the premise of not significantly increasing the residual displacement, the device can significantly improve the energy dissipation capacity of the structure and effectively reduce the peak displacement angle of the structure, providing a new idea and method for solving the related problems of the truss string structure under the action of earthquakes.

[0007] In summary, according to the above comprehensive analysis, in order to prevent the buckling problem of the sleeve in the truss string structure, it is urgent to develop a truss string anti-collapse device that can effectively improve the energy dissipation and yield stiffness of the member. At the same time, the device also needs to fully consider the recoverable performance of the truss string under the seismic environment to ensure that the structure can maintain sufficient stability and safety when facing various complex working conditions, and can quickly restore functionality after the disaster and reduce losses. SUMMARY

[0008] In order to avoid and overcome the technical problems existing in the prior art, the present application provides a partial self-centering friction damping double sleeve device and a device parameter calculation method. The present application effectively solves the problems of buckling, insufficient energy dissipation and small stiffness of the truss string structure through the innovative combination of double sleeve design, planar friction damper and recoverable slope friction damper, and significantly improves the recoverable performance of the structure under the action of earthquakes or accidental gravity loads.

[0009] To achieve the above object, the present application provides the following technical scheme:

[0010] A partial self-centering friction damping double sleeve device, comprising a sleeve installed in a truss string structure, the sleeve comprising an inner sleeve and an outer sleeve coaxially sleeved with each other; two groups of recoverable slope friction dampers and two groups of planar friction dampers are installed between the inner sleeve and the outer sleeve, and the two groups of recoverable slope friction dampers and the two groups of planar friction dampers are sequentially and spacedly arranged around the outer sleeve in a cross shape; the recoverable slope friction dampers and the planar friction dampers can cooperate to generate a reverse force for consuming the potential energy of the relative axial deformation between the inner sleeve and the outer sleeve and restoring the inner sleeve and the outer sleeve axially.

[0011] As a further aspect of the present invention: the recoverable slope friction damper includes a first bolt vertically fixed to the outer wall of the inner sleeve, a steel washer sandwiched between the inner sleeve and the outer sleeve, a recoverable friction inner plate fixedly installed on the outer wall of the outer sleeve, and a recoverable friction outer plate fitted onto the outer surface of the recoverable friction inner plate; the mating surfaces of the recoverable friction outer plate and the recoverable friction inner plate form an isosceles trapezoidal tooth meshing form, and this meshing form extends along the axial direction of the outer sleeve; the head of the first bolt sequentially passes through a circular hole on the steel washer and a long... The inner and outer plates of the reversible friction plate have a long slot, a round hole, and a central hole of the first disc spring. These are threaded together with the first nut to press the outer plate of the reversible friction plate onto the inner plate of the reversible friction plate using the elastic force of the first disc spring. The long slot on the outer sleeve and the inner plate of the reversible friction plate overlap each other and extend along the axial direction of the outer sleeve. This allows the outer sleeve and the inner plate of the reversible friction plate to perform an axially elastically reciprocating sliding motion relative to the inner sleeve, the steel washer, the outer plate of the reversible friction plate, and the first bolt when the inner sleeve is subjected to axial force.

[0012] As a further embodiment of the present invention: the planar friction damper includes a non-asbestos organic gasket sandwiched between the inner sleeve and the outer sleeve, a planar friction plate slidably mounted on the outer wall of the outer sleeve, and a second bolt vertically fixed to the outer wall of the inner sleeve; the head of the second bolt passes through a round hole on the non-asbestos organic gasket, an elongated hole on the outer sleeve, a round hole on the planar friction plate, and the center hole of the second disc spring in sequence, and is threadedly connected to the second nut; the elongated holes on the outer sleeve and the planar friction plate coincide with each other and both extend along the axial direction of the outer sleeve, so that when the inner sleeve is subjected to axial force, the outer sleeve performs an axial reciprocating sliding action relative to the inner sleeve, the non-asbestos organic gasket, the planar friction plate, and the second bolt.

[0013] As a further aspect of the present invention: multiple first bolts are provided in the same recoverable slope friction damper, and each first bolt is inserted into the corresponding round hole and elongated hole, and arranged equidistantly along the axial direction of the outer sleeve; multiple second bolts are provided in the same planar friction damper, and each second bolt is inserted into the corresponding round hole and elongated hole, and arranged equidistantly along the axial direction of the outer sleeve.

[0014] As a further aspect of the present invention: the surfaces of the reversible friction inner plate and the flat friction plate that are in contact with the outer tube are all arc surfaces, and the curvature of the arc surfaces is the same as the curvature of the outer wall surface of the outer tube.

[0015] As a further aspect of the present invention, multiple anti-bending devices are installed between the inner sleeve and the outer sleeve, and each anti-bending device is arranged evenly in sequence along the circumference of the inner sleeve.

[0016] As a further embodiment of the present invention: each anti-buckling device arranged uniformly along the circumference of the inner sleeve constitutes a group of anti-buckling devices, and multiple groups of anti-buckling devices are arranged uniformly along the axial direction of the inner sleeve.

[0017] A method for calculating device parameters, applied to the aforementioned partially self-resetting friction damping double-sleeve device, includes the following calculation steps:

[0018] S1. Determine the friction coefficient of each group of recoverable slope friction dampers (20). The number of the first bolt (21) and the slope angle of the isosceles trapezoidal teeth. and order Simultaneously determine the friction coefficient in each group of planar friction dampers (30). The number of second bolts (33) and diameter;

[0019] S2. Determine the model of the first disc spring (25) according to the diameter of the first bolt (21), and install multiple first disc springs (25) on the same first bolt (21) to form a first disc spring group; the number of springs stacked in the first disc spring group is The number of pairs is At the same time, axial preload is applied to each of the first disc spring assemblies. ;

[0020] S3. Determine the maximum load of the first disc spring (25) according to its model number. and maximum deformation And calculate the stiffness of the first disc spring (25) in each set of recoverable slope friction dampers (20). ;

[0021] ;

[0022] S4, Based on axial preload Calculate the starting load for each set of recoverable slope friction dampers (20). ;

[0023] ;

[0024] S5. Determine the stiffness of the inner sleeve (11) and the outer sleeve (12). and And calculate the starting stiffness of each set of recoverable slope friction dampers (20). ;

[0025] ;

[0026] S6. Calculate the starting displacement of each group of recoverable slope friction dampers (20) based on the starting load and starting stiffness. ;

[0027] ;

[0028] S7. Based on the deformation requirements of the tensioned truss, determine the maximum deformation of the entire device as follows: Then calculate the maximum load of each group of recoverable slope friction dampers (20) at maximum deformation of the entire device. and reverse starting force ;

[0029] ;

[0030] ;

[0031] S8. Determine the partial self-reset efficiency of the entire device. And calculate the reverse load of each group of recoverable slope friction dampers (20) at this time. And the reverse load at this time This is the starting load for each set of planar friction dampers (30). ;

[0032] ;

[0033] S9. Determine the model of the second disc spring (34) according to the diameter of the second bolt (33) in each group of planar friction dampers (30), and install multiple second disc springs (34) on the same second bolt (33) to form a second disc spring group; the number of springs stacked in the second disc spring group is The number of pairs is At the same time, axial preload is applied to each of the second disc spring assemblies. ;

[0034] ;

[0035] S10. Determine the maximum load of the second disc spring (34) according to its model number. and maximum deformation ;like If the above parameters are set correctly, then the settings meet the requirements; otherwise, they need to be readjusted. , and until satisfied .

[0036] As a further aspect of the present invention: the friction coefficient of the recoverable slope friction damper is the friction coefficient between steel and steel; the friction coefficient of the planar friction damper is the friction coefficient between steel and non-asbestos organic pad.

[0037] As a further aspect of the present invention: The value is 0.16. The value is 0.33.

[0038] Compared with the prior art, the beneficial effects of the present invention are:

[0039] 1. Through a double-sleeve design, the inner and outer sleeves work together to provide fundamental structural support for the entire device. An innovative combination of planar friction dampers and recoverable slope friction dampers, arranged in a cross shape around the circumference of the sleeve, can comprehensively address the axial deformation of the inner sleeve. Under earthquakes or unexpected gravity loads, the recoverable slope friction dampers and planar friction dampers work together to dissipate the axial deformation energy of the inner sleeve, effectively solving the buckling problem of the tensioned truss structure. Simultaneously, their energy dissipation capacity compensates for the structure's insufficient energy dissipation, and the increased stiffness makes the structure more stable. Furthermore, they can generate a reverse force to reset the inner sleeve, significantly enhancing the structure's recoverability under special loads and ensuring the safety and reusability of the tensioned truss structure under extreme conditions.

[0040] 2. The isosceles trapezoidal tooth meshing surface of the recoverable slope friction damper generates a unique mechanical effect under stress. The first bolt sequentially passes through multiple components and is threadedly connected to the first nut. This, combined with the elastic force of the first disc spring, presses the recoverable outer friction plate and the recoverable inner friction plate together, creating a stable frictional force. When the inner sleeve is subjected to axial force, the outer sleeve and the recoverable inner friction plate can slide axially. During this process, the relative motion of the isosceles trapezoidal tooth surface dissipates energy through friction. Simultaneously, the geometric characteristics of the tooth surface generate a component force opposite to the deformation direction of the inner sleeve, aiding in the inner sleeve's reset. This provides a crucial mechanism for the device's energy dissipation and self-resetting functions.

[0041] 3. The non-asbestos organic gasket in the planar friction damper has good frictional performance and a certain degree of elasticity, which can effectively increase friction and buffer part of the impact force. The planar friction plate is slidably installed on the outer wall of the outer sleeve and connected to the inner sleeve by a second bolt and a second disc spring. When the inner sleeve is subjected to axial force, the outer sleeve and the planar friction plate slide relative to each other, using the friction between the steel and the non-asbestos organic gasket to consume energy. This compensates for the insufficient energy consumption of the recoverable slope friction damper in different directions or under different working conditions. Working together with the recoverable slope friction damper, it improves the overall energy consumption capacity of the device, ensuring effective energy consumption under various conditions and reducing structural deformation.

[0042] 4. Multiple first bolts equidistantly arranged along the axial direction of the outer casing are incorporated into the same recoverable slope friction damper. This ensures more uniform axial stress distribution on components such as the recoverable outer and inner friction plates, preventing localized stress concentrations that could lead to component damage. The multi-bolt design increases connection points, improves overall load-bearing capacity, and better transmits and disperses force, ensuring stable operation of the recoverable slope friction damper even under heavy loads. Similarly, multiple equidistant second bolts in the planar friction damper serve the same purpose, enhancing its reliability and stability, thereby improving the overall performance of the device.

[0043] 5. The arc-shaped design of the inner friction plate and flat friction plate in contact with the outer sleeve increases the contact area and ensures uniform distribution. During operation, this design effectively reduces contact stress, minimizes component wear, and extends component lifespan. Simultaneously, the tight and uniform contact facilitates more stable force transmission, ensuring the stability and reliability of the friction damper. This guarantees the friction damper functions correctly under various operating conditions, maintaining the overall stability of the device's performance.

[0044] 6. Buckling arrestors are arranged sequentially along the axial direction of the outer sleeve, providing additional restraint and support to both the inner and outer sleeves. Under heavy loads, these arrestors prevent buckling deformation of the inner and outer sleeves, maintaining the structure's geometry and load-bearing capacity. This not only enhances the stability of the arrestor itself but also ensures the normal operation of the planar friction damper and the recoverable slope friction damper, preventing damper failure due to sleeve buckling. This improves the safety and reliability of the entire structure under complex stress conditions.

[0045] 7. This calculation method starts by determining fundamental parameters such as the friction coefficient and considers the material properties of the friction damper. By determining the slope angle, the mechanical performance of the recoverable slope friction damper is optimized. The number of bolts, spring-related parameters, and various loads and displacements are calculated, comprehensively considering the mechanical response of the device at different working stages. Based on the deformation requirements of the tensioned truss, the maximum deformation and related loads are determined, ensuring that the designed device accurately meets the performance requirements of tensioned truss structures in actual engineering, thus ensuring the effectiveness and reliability of the device in practical applications.

[0046] 8. Clearly define the material combinations corresponding to the friction coefficients of different friction dampers, enabling designers to make more informed material selections. For recoverable slope friction dampers, the friction coefficient between steel is used, facilitating accurate calculations based on steel properties and engineering experience. For planar friction dampers, the friction coefficient between steel and non-asbestos organic gaskets is determined, ensuring that the influence of material factors on friction performance is accurately considered during design and calculation, thereby improving the accuracy and reliability of device performance calculations.

[0047] 9. Specific friction coefficient values ​​are provided, offering designers a clear data standard. During the design process, there is no need to spend significant time and effort determining the range of the friction coefficient; the given values ​​can be used directly for calculations, reducing design errors caused by parameter uncertainties. This results in better consistency and comparability of devices designed by different designers, improving design efficiency and ensuring the stability and reliability of the device's performance. Attached Figure Description

[0048] Figure 1 This is a schematic diagram of the overall structure of the device of the present invention.

[0049] Figure 2 This is a schematic diagram of the end view structure of the device of the present invention.

[0050] Figure 3 This is a schematic diagram of the mating structure of the reversible friction inner plate and the reversible friction outer plate in this invention.

[0051] Figure 4 This is a schematic diagram of the reversible friction outer plate in this invention.

[0052] Figure 5 This is a schematic diagram of the reversible friction inner plate in this invention.

[0053] Figure 6 This is a cross-sectional view of the sleeve in this invention.

[0054] Figure 7 This is a schematic diagram illustrating the steps of the method in this invention.

[0055] In the diagram: 10. Sleeve; 11. Inner sleeve; 12. Outer sleeve; 20. Recoverable slope friction damper; 21. First bolt; 22. Steel washer; 23. Recoverable friction inner plate; 24. Recoverable friction outer plate; 25. First disc spring; 26. First nut; 30. Planar friction damper; 31. Non-asbestos organic gasket; 32. Planar friction plate; 33. Second bolt; 34. Second disc spring; 35. Second nut; 40. Anti-buckling device. Detailed Implementation

[0056] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0057] Please see Figures 1-7 The usage process of the device of the present invention is as follows:

[0058] I. Preliminary Preparations

[0059] 1. Determine structural parameters

[0060] Based on the specific design requirements of the tensioned truss structure, the dimensions of the inner sleeve 11 and the outer sleeve 12 are precisely determined. Factors such as the structure's load-bearing capacity, deformation requirements, and installation space are considered. For example, if the tensioned truss is used in a large-span stadium building, the inner sleeve 11 can be a seamless steel pipe with a diameter of 200mm and a wall thickness of 10mm, while the outer sleeve 12 has a diameter of 250mm and a wall thickness of 12mm. Both are made of Q345B steel, which has excellent comprehensive mechanical properties and can meet the strength and stiffness requirements of the structure under various loads.

[0061] Based on the expected energy consumption and self-resetting performance of the device, the layout and parameters of the recoverable slope friction damper 20 and the planar friction damper 30 are planned in detail. Combining theoretical calculations and engineering experience, the specific dimensions of the isosceles trapezoidal teeth in the recoverable slope friction damper 20 are determined, such as a waist length of 50 mm and a slope angle of 45°; the area and thickness of the friction plate in the planar friction damper 30 are determined, such as a friction plate area of ​​5000 mm² and a thickness of 10 mm, to ensure that the two dampers can achieve the best effect when working together.

[0062] 2. Selection of structural materials

[0063] Materials such as inner sleeve 11, outer sleeve 12, bolts, washers, friction plates, and disc springs were procured strictly in accordance with design requirements. A spectrometer was used to analyze the chemical composition of the steel, and a universal testing machine was used to test its tensile strength, yield strength, elongation, and other mechanical properties to ensure that all indicators met national standards and design requirements.

[0064] For disc springs, select a professional spring manufacturer and request a report on the mechanical performance parameters of the product. Conduct random sampling inspections on each batch of disc springs, using a spring testing machine to test key performance indicators such as spring stiffness, maximum load, and deformation, to ensure stable and reliable spring quality.

[0065] II. Component Processing and Manufacturing

[0066] 1. Inner and outer tubing processing

[0067] Machining of inner sleeve 11: The inner sleeve 11 is machined using a high-precision CNC lathe to ensure that the inner and outer diameter dimensions of the inner sleeve 11 are controlled within ±0.05mm.

[0068] Machining of the outer sleeve 12: The outer sleeve 12 is also machined using a CNC lathe to ensure that the clearance between the inner diameter of the outer sleeve 12 and the outer diameter of the inner sleeve 11 is between 0.5-1mm, satisfying both axial sliding requirements and ensuring a certain degree of coaxiality. At corresponding positions on the outer sleeve 12, a milling machine is used to machine elongated holes and round holes. The length of the elongated holes is determined based on the maximum axial displacement of the inner sleeve 11, generally 20-30mm larger than the maximum displacement, and the width is 2-3mm larger than the bolt diameter to ensure smooth sliding between the outer sleeve 12 and the relevant friction plates under axial force.

[0069] 2. Machining of friction damper components

[0070] The recoverable slope friction damper 20 consists of two components: a recoverable inner friction plate 23 and a recoverable outer friction plate 24, which are cut using a CNC cutting machine and then machined into isosceles trapezoidal tooth meshing surfaces using a milling and grinding machine. The machining accuracy of the tooth surface is controlled within ±0.05mm, and the surface roughness reaches Ra3.2μm to ensure good friction performance and meshing effect. On the recoverable inner friction plate 23, elongated holes are drilled according to design requirements to mate with the first bolt 21; on the recoverable outer friction plate 24, circular holes are drilled according to design requirements to mate with the first bolt 21. The positional accuracy of the holes is controlled within ±0.1mm. The first bolt 21 is made of high-strength alloy steel, such as 40Cr steel, and undergoes heat treatment to achieve a hardness of HRC30-35, improving the bolt's overall mechanical properties. After the recoverable inner friction plate 23 is cut using a CNC cutting machine, an arc surface that fits with the outer sleeve 12 is machined using a milling machine. The curvature of the arc surface is consistent with the curvature of the outer wall surface of the outer sleeve 12.

[0071] The planar friction damper 30 consists of a non-asbestos organic gasket 31, which is formed by die stamping according to design dimensions to ensure dimensional accuracy and thickness uniformity. The planar friction plate 32 is cut using a CNC cutting machine and then milled to form an arc surface that fits against the outer sleeve 12. The curvature of the arc surface matches the curvature of the outer wall of the outer sleeve 12, with a deviation controlled within ±0.05mm. An elongated hole is drilled on the planar friction plate 32 to mate with the second bolt 33; the machining accuracy of the hole is the same as that of the recoverable friction inner plate 23. The material and processing technology of the second bolt 33 are the same as those of the first bolt 21.

[0072] III. Device Assembly

[0073] 1. Assembly of reversible slope friction damper

[0074] The first bolt 21 is sequentially passed through the steel washer 22, the elongated hole on the outer sleeve 12, the elongated hole on the restorable friction inner plate 23, the round hole on the restorable friction outer plate 24, and the center hole of the first disc spring 25. The tail of the first bolt 21 is welded to the outer wall of the inner sleeve 11. During assembly, ensure that the holes of each component are aligned to avoid the bolt being tilted and subjected to force.

[0075] Tighten the first nut 26 onto the other end of the first bolt 21 using a torque wrench to tighten it to the designed preload. For example, the preload of the first disc spring 25 is calculated to be 800 N•m. During tightening, the torque error is controlled within ±5% to ensure that the recoverable friction outer plate 24 is tightly pressed against the recoverable friction inner plate 23, providing stable friction.

[0076] The assembled recoverable slope friction damper 20 is arranged at equal angular intervals around the inner sleeve 11 according to the design requirements, usually at 90° intervals. Positioning fixtures are used to ensure that the installation position is accurate, and then it is temporarily fixed.

[0077] 2. Assembly of plane friction damper

[0078] Place the non-asbestos organic gasket 31 onto the second bolt 33 and check whether the gasket is intact, without damage or deformation.

[0079] The second bolt 33 is passed through the non-asbestos organic gasket 31, the elongated hole on the outer sleeve 12, the round hole on the flat friction plate 32, and the center hole of the second disc spring 34 in sequence. The tail of the second bolt 33 is vertically welded to the outer wall of the inner sleeve 11 to ensure that the installation sequence of each component is correct.

[0080] Tighten the second nut 35 onto the other end of the second bolt 33 using a torque wrench according to the designed preload. For example, if the preload is 600 N•m, the torque error should also be controlled within ±5%.

[0081] The assembled planar friction dampers 30 are installed between the recoverable slope friction dampers 20 in a cross shape. During the installation process, the position and connection of each component are checked again to ensure that the overall layout of the device is reasonable.

[0082] 3. Install anti-buckling devices

[0083] The buckling restraint device 40 is a steel pipe that is sleeved and clamped between the inner sleeve 11 and the outer sleeve 12, dividing the entire pressure-bearing section of the sleeve 10 into multiple pressure-bearing sections, reducing the length of each pressure-bearing section and improving the buckling resistance. The buckling restraint device 40 can also be multiple long strips cut from the steel pipe, with each long strip arranged evenly along the circumference of the inner sleeve 11 to form a buckling restraint group, and then multiple buckling restraint groups arranged evenly along the axial direction of the inner sleeve 11.

[0084] Between the inner sleeve 11 and the outer sleeve 12, anti-buckling devices 40 are installed sequentially along the axial direction of the inner sleeve 11 at the designed spacing, and the installation positions of the anti-buckling devices 40 are marked with positioning marks to ensure accurate installation.

[0085] The buckling arrestor 40 is fixed to the inner and outer sleeves 12 by welding or high-strength bolts. If welding is used, the welding area on the outer wall of the inner sleeve 11 is cleaned and preheated before welding. During welding, welding parameters such as welding current, voltage and welding speed are strictly controlled to ensure welding quality. If bolts are used, a torque wrench is used to tighten the bolts to the designed torque to ensure a firm and reliable connection.

[0086] 4. Overall inspection and debugging

[0087] After the device is assembled, a comprehensive inspection of the overall structure is carried out. Check whether the connections of each component are secure, whether the bolts are tightened, and whether there are any missing or incorrectly installed components. Use a feeler gauge to check the gaps between the restorable friction outer plate 24 and the restorable friction inner plate 23, and between the flat friction plate 32 and the non-asbestos organic gasket 31, to ensure that the gaps are uniform and there are no areas that are too large or too small.

[0088] The device undergoes initial debugging by applying a small axial force to the inner sleeve 11 to simulate minute deformations during actual operation. This checks the smooth sliding of the outer sleeve 12 and the friction plate, identifying any jamming issues. Displacement and force sensors are used to measure the displacement and force of the device during loading, recording the data and analyzing the initial performance. Any problems discovered are promptly addressed.

[0089] IV. Installation to the tensioned truss structure

[0090] 1. Preparations before installation

[0091] On-site measurements and cleaning were conducted at the designed installation location of the tensioned truss structure. A total station was used to measure the dimensions and coordinates of the installation location to ensure they matched the installation dimensions of the device. Debris, oil, rust, and other contaminants were removed from the installation location to ensure a smooth and clean surface, providing a good foundation for the device installation.

[0092] Select appropriate lifting equipment, such as a truck crane or tower crane, based on the weight and size of the installation. Conduct a comprehensive inspection and testing of the lifting equipment to ensure its good performance and reliability. Prepare lifting slings, such as wire ropes, hooks, and shackles. The specifications and load-bearing capacity of the slings should meet the lifting requirements of the installation and have undergone rigorous inspection and testing.

[0093] 2. Equipment hoisting and installation

[0094] The assembled self-resetting friction damping double sleeve 10 device was hoisted to the installation position of the tensioned truss structure using hoisting equipment. During the hoisting process, a designated person was assigned to direct the operation to ensure its safety and stability. A traction rope was used to control the device's swing and prevent collisions with surrounding structures.

[0095] Connect the inner sleeve 11 and outer sleeve 12 of the device to the corresponding components of the tensioned truss structure. The connection method can be selected according to design requirements, such as welding, bolting, or pin connection. If welding is used, welding operations should be carried out according to the welding process specifications. After welding, non-destructive testing, such as ultrasonic testing or radiographic testing, should be performed to ensure that the welding quality meets the standards. If bolting is used, tighten the bolts with a torque wrench according to the design torque and install anti-loosening devices, such as spring washers or anti-loosening nuts, to prevent the bolts from loosening.

[0096] 3. Post-installation inspection and acceptance

[0097] After the device is installed, the connection between the device and the tensioned truss structure is checked again to ensure that the connection is firm and there is no looseness. The overall verticality and horizontality of the device are checked using a theodolite and a level. The verticality deviation is controlled within ±5mm and the horizontal deviation is controlled within ±3mm. If they exceed the allowable range, adjustments are made in time.

[0098] A comprehensive acceptance test was conducted on the device in accordance with relevant acceptance standards and specifications. The acceptance included aspects such as the device's appearance quality, installation dimensions, connection reliability, and mechanical performance. A loading test was performed on the device to simulate the load conditions that a tensioned truss structure might experience in actual use. Displacement gauges, force sensors, and other detection equipment were used to measure the device's displacement, stress, and energy consumption to verify whether the device met the design requirements. Upon successful acceptance, an acceptance report was issued, recording all acceptance data and results.

[0099] like Figure 7 As shown, based on the above working principle and structure, the following method is proposed for calculating the device parameters of the partially self-resetting friction damping double sleeve 10 device:

[0100] S1. Determine the friction coefficient of each group of recoverable slope friction dampers 20. The coefficient of friction of the planar friction damper 30 Determine the slope angle of the isosceles trapezoidal teeth of each set of recoverable slope friction dampers. To prevent self-locking of the friction surface (i.e., the axial force cannot push the slope to slide), the tangent of the slope angle must be greater than the coefficient of friction to ensure that the damper can slide and dissipate energy normally during deformation. Determine the number of the first bolts 21 in each group of recoverable slope friction dampers 20. And the diameter, while determining the number of second bolts 33 in each group of planar friction dampers 30. and diameter;

[0101] S2. Determine the model of the first disc spring 25 according to the diameter of the first bolt 21, and install multiple first disc springs 25 on the same first bolt 21 to form a first disc spring group; the number of springs stacked in the first disc spring group is... The number of pairs is At the same time, axial preload is applied to each of the first disc spring assemblies. The arrangement of the first disc spring 25 in terms of engagement and overlap can be random or arranged in a uniformly spaced manner.

[0102] S3. Determine the maximum load of the first disc spring 25 according to its model number. and maximum deformation And calculate the stiffness of the first disc spring 25 in each set of recoverable slope friction dampers 20. ;

[0103] ;

[0104] S4, Based on preload Calculate the starting load for each set of recoverable slope friction dampers 20. ;

[0105] ;

[0106] S5. Determine the stiffness of the inner sleeve 11 and the outer sleeve 12. and And calculate the starting stiffness of each set of recoverable slope friction dampers 20. ;

[0107] ;

[0108] S6. Calculate the starting displacement of each group of recoverable slope friction dampers 20 based on the starting load and starting stiffness. ;

[0109] ;

[0110] S7. Based on the deformation requirements of the tensioned truss, determine the maximum deformation of the entire device as follows: Then, calculate the maximum load on each group of recoverable slope friction dampers 20 when the entire device is under maximum deformation. and reverse starting force ;

[0111] ;

[0112] ;

[0113] S8. Determine the partial self-reset efficiency of the entire device. And calculate the reverse load of each group of recoverable slope friction dampers 20 at this time. And the reverse load at this time This is the starting load of each set of planar friction dampers 30. ;

[0114] ;

[0115] S9. Determine the model of the second disc spring 34 based on the diameter of the second bolt 33 in each group of planar friction dampers 30, and install multiple second disc springs 34 on the same second bolt 33 to form a second disc spring group; the number of springs stacked in the second disc spring group is... The number of pairs is The arrangement of the second disc springs 34 in conjunction and overlap can be random or evenly spaced. Simultaneously, an axial preload is applied to each second disc spring assembly. ;

[0116] ;

[0117] S10. Determine the maximum load of the second disc spring 34 according to its model number. and maximum deformation ;like If the above parameters are set correctly, then the settings meet the requirements; otherwise, they need to be readjusted. , and until satisfied .

[0118] Taking the lower chord of a single-chord truss as an example, its maximum allowable axial deformation is 20mm, which can restore the friction coefficient of the slope friction damper 20. The coefficient of friction of the planar friction damper 30 is 0.16. It is 0.33. Preliminary determination. Satisfying greater than Requirements.

[0119] Further determine the number of the first bolts 21 in the recoverable slope friction damper 20 The number of second bolts 33 in the plane friction damper 30 Both types of bolts are M20 high-strength bolts of grade 8.8.

[0120] Based on the bolt type, both the recoverable slope friction damper 20 and the plane friction damper 30 use A-series disc springs with an inner diameter of 20.4mm and an outer diameter of 40mm. This means the first and second disc spring groups use the same disc spring model. According to the standard "Disc Springs (GB / T1972-2005)," the maximum load of this disc spring model can be found in the table. Maximum deformation The number of overlapping and mating elements in each of the first disc spring assemblies of the recoverable slope friction damper 20 is determined as follows: and The preload applied by each first disc spring assembly Therefore, the stiffness of the first disc spring 25 in the recoverable slope friction damper 20 can be calculated. .

[0121] Furthermore, the starting stiffness of a single recoverable slope friction damper 20 is calculated. The starting load of a single recoverable slope friction damper 20 Therefore, the starting displacement of a single recoverable slope friction damper 20 .

[0122] Furthermore, the maximum load when the recoverable slope friction damper 20 undergoes a maximum deformation of 20 mm is calculated as follows: and reverse starting force .

[0123] As required, part of the self-resetting efficiency will be reduced. Set to 0.5, meaning the load on the self-resetting friction damping double-sleeve device 10 for the tensioned truss structure resisting progressive collapse is 0 when the thickness is 10mm. The reverse load of the recoverable slope friction damper 20 is 7.12kN. At this time, the starting load of the plane friction damper 30 is... .

[0124] Further calculations were performed on the preload applied by a single first disc spring assembly. Further calculations were performed on the number of stacked and engaged second disc spring groups in the planar friction damper 30. and The calculation results satisfy The design is now complete.

[0125] The above description is only a preferred embodiment of the present invention, but the scope of protection of the present invention is not limited thereto. Any equivalent substitutions or modifications made by those skilled in the art within the scope of the technology disclosed in the present invention, based on the technical solution and inventive concept of the present invention, should be covered within the scope of protection of the present invention.

Claims

1. A partially self-resetting friction damping double-sleeve device, characterized in that, The structure includes a sleeve (10) installed in a tensioned truss structure. The sleeve (10) includes an inner sleeve (11) and an outer sleeve (12) that are coaxially connected to each other. Two sets of recoverable slope friction dampers (20) and two sets of planar friction dampers (30) are installed between the inner sleeve (11) and the outer sleeve (12), and the two are arranged alternately around the outer sleeve (12) in a cross-shaped distribution. The recoverable slope friction dampers (20) and the planar friction dampers (30) can cooperate to generate a counterforce to consume the relative axial deformation potential energy between the inner sleeve (11) and the outer sleeve (12) and to restore the axial direction of the inner sleeve (11) and the outer sleeve (12). The surface friction damper (20) includes a first bolt (21) vertically fixed to the outer wall of the inner sleeve (11), a steel washer (22) sandwiched between the inner sleeve (11) and the outer sleeve (12), a recoverable friction inner plate (23) fixedly installed on the outer wall of the outer sleeve (12), and a recoverable friction outer plate (24) fitted onto the outer plate surface of the recoverable friction inner plate (23); the mating surfaces of the recoverable friction outer plate (24) and the recoverable friction inner plate (23) are in the form of isosceles trapezoidal tooth meshing, and this meshing form extends along the axial direction of the outer sleeve (12); the head of the first bolt (21) passes through the round hole on the steel washer (22) and the outer sleeve (12) in sequence. The outer sleeve (12) and the inner reversible friction plate (23) have elongated holes, the inner reversible friction plate (23) have elongated holes, the outer reversible friction plate (24) has round holes, and the center hole of the first disc spring (25) are threaded together with the first nut (26) to press the outer reversible friction plate (24) onto the inner reversible friction plate (23) by the elastic force of the first disc spring (25); the elongated holes on the outer sleeve (12) and the inner reversible friction plate (23) coincide with each other and extend along the axial direction of the outer sleeve (12) so that when the inner sleeve (11) is subjected to axial force, the outer sleeve (12) and the inner reversible friction plate (23) are relative to the inner sleeve (11), the steel gasket (22), and the outer reversible friction plate (24). The plate (24) and the first bolt (21) perform axial elastic reset reciprocating sliding action; the plane friction damper (30) includes a non-asbestos organic gasket (31) sandwiched between the inner sleeve (11) and the outer sleeve (12), a plane friction plate (32) slidably installed on the outer wall of the outer sleeve (12), and a second bolt (33) vertically fixed to the outer wall of the inner sleeve (11); the head of the second bolt (33) passes through the round hole on the non-asbestos organic gasket (31), the elongated hole on the outer sleeve (12), the round hole on the plane friction plate (32), and the center hole of the second disc spring (34) in sequence, and is threadedly connected to the second nut (35);The elongated holes on the outer sleeve (12) and the flat friction plate (32) overlap and extend axially along the outer sleeve (12), so that when the inner sleeve (11) is subjected to axial force, the outer sleeve (12) reciprocates axially relative to the inner sleeve (11), the non-asbestos organic gasket (31), the flat friction plate (32), and the second bolt (33).

2. The partially self-resetting friction damping double-sleeve device according to claim 1, characterized in that, Multiple first bolts (21) are provided in the same recoverable slope friction damper (20), and each first bolt (21) is inserted into the corresponding round hole and elongated hole, and arranged equidistantly along the axial direction of the outer sleeve (12); multiple second bolts (33) are provided in the same planar friction damper (30), and each second bolt (33) is inserted into the corresponding round hole and elongated hole, and arranged equidistantly along the axial direction of the outer sleeve (12).

3. The partially self-resetting friction damping double-sleeve device according to claim 2, characterized in that, The surfaces of the reversible friction inner plate (23) and the flat friction plate (32) that are in contact with the outer tube are all arc surfaces, and the curvature of the arc surfaces is the same as the curvature of the outer wall surface of the outer tube (12).

4. The partially self-resetting friction damping double-sleeve device according to claim 3, characterized in that, Multiple anti-buckling devices (40) are also installed between the inner sleeve (11) and the outer sleeve (12), and each anti-buckling device (40) is arranged evenly along the circumference of the inner sleeve (11).

5. A partially self-resetting friction damping double-sleeve device according to claim 4, characterized in that, Each buckling protection device (40) arranged in sequence along the circumference of the inner sleeve (11) constitutes a buckling protection group, and multiple buckling protection groups are arranged in sequence along the axial direction of the inner sleeve (11).

6. A method for calculating device parameters, wherein the method is applied to a partially self-resetting friction damping double-sleeve device as described in claim 5, characterized in that, The calculation steps include the following: S1. Determine the friction coefficient of each group of recoverable slope friction dampers (20). The number of the first bolt (21) and the slope angle of the isosceles trapezoidal teeth. and order Simultaneously determine the friction coefficient in each group of planar friction dampers (30). The number of second bolts (33) and diameter; S2. Determine the model of the first disc spring (25) according to the diameter of the first bolt (21), and install multiple first disc springs (25) on the same first bolt (21) to form a first disc spring group; the number of springs stacked in the first disc spring group is The number of pairs is At the same time, axial preload is applied to each of the first disc spring assemblies. ; S3. Determine the maximum load of the first disc spring (25) according to its model number. and maximum deformation And calculate the stiffness of the first disc spring (25) in each set of recoverable slope friction dampers (20). ; ； S4, Based on axial preload Calculate the starting load for each set of recoverable slope friction dampers (20). ; ； S5. Determine the stiffness of the inner sleeve (11) and the outer sleeve (12). and And calculate the starting stiffness of each set of recoverable slope friction dampers (20). ; ； S6. Calculate the starting displacement of each group of recoverable slope friction dampers (20) based on the starting load and starting stiffness. ; ； S7. Based on the deformation requirements of the tensioned truss, determine the maximum deformation of the entire device as follows: Then calculate the maximum load of each group of recoverable slope friction dampers (20) at maximum deformation of the entire device. and reverse starting force ; ； ； S8. Determine the partial self-reset efficiency of the entire device. And calculate the reverse load of each group of recoverable slope friction dampers (20) at this time. And the reverse load at this time This is the starting load for each set of planar friction dampers (30). ; ; S9. Determine the model of the second disc spring (34) according to the diameter of the second bolt (33) in each group of planar friction dampers (30), and install multiple second disc springs (34) on the same second bolt (33) to form a second disc spring group; the number of springs stacked in the second disc spring group is The number of pairs is At the same time, axial preload is applied to each of the second disc spring assemblies. ; ； S10. Determine the maximum load of the second disc spring (34) according to its model number. and maximum deformation ;like If the above parameters are set correctly, then the settings meet the requirements; otherwise, they need to be readjusted. , and until satisfied .

7. The method for calculating device parameters according to claim 6, characterized in that, The friction coefficient of the recoverable slope friction damper (20) is the friction coefficient between steel and steel; the friction coefficient of the planar friction damper (30) is the friction coefficient between steel and non-asbestos organic pad (31).

8. The method for calculating device parameters according to claim 7, characterized in that, The value is 0.

16. The value is 0.33.

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