A pre-stressed anti-chopping hammer and a pre-stressed determination method and system

Abstract

The application provides a pre-stressed anti-vibration hammer and a pre-stressed determination method and system, which comprise a gap type steel strand, an assembled integral hammer head and an anchoring clamp; the gap type steel strand comprises a center layer circular wire, an intermediate layer profiled wire and an outer layer circular wire from inside to outside; a gap is arranged between the center layer circular wire and the intermediate layer profiled wire, the gap is filled with lubricating grease, the frictional resistance between the center layer circular wire and the intermediate layer profiled wire is reduced, and the center layer circular wire is pre-stressed; the intermediate layer profiled wire is in an arch body structure, the arch body structure increases the polar moment of inertia, and the bending stiffness of the steel strand is enhanced; the center layer circular wire is connected with the assembled integral hammer head at both ends, and the anchoring clamp is assembled in a hollow portion of the assembled integral hammer head away from the center layer circular wire, and is used for clamping the center layer circular wire with a pre-stressed target stress; the tensile stress generated by the impact load can first offset the tensile stress formed between the outer layer circular wire and the intermediate layer strand after the pre-stress, and the bending stiffness of the steel strand is increased.

Description

Technical Field

[0001] This invention relates to the field of vibration damping devices for power transmission lines, specifically to a prestressed vibration damper and a method and system for determining the prestress. Background Technology

[0002] In areas with strong winds, power transmission lines are subjected to significant impacts from wind galloping. Under such impacts, the lines may vibrate, sway, or deform, leading to fatigue of the conductor material. In severe cases, this can even result in strand breakage or line breakage. Therefore, vibration dampers are typically installed on power transmission lines to absorb or reduce vibration energy, change the line swaying frequency, prevent line vibration or galloping, and keep the conductors in a relatively stable state.

[0003] Current designs for the bending stiffness of vibration damper steel strands are based on meeting the vibration damping performance under light wind vibration conditions, and are suitable for the dynamic response of conductors under light wind vibration conditions. However, under the action of large impact loads in strong wind areas, the steel strands of the vibration damper on the conductor are prone to significant plastic deformation due to insufficient bending stiffness, which affects its vibration damping effect. Furthermore, existing dynamic characteristic testing methods for vibration dampers are also based on light wind vibration conditions, and the range of values ​​for the bending stiffness and damping coefficient of the vibration damper steel strands is not applicable to the calculation of the dynamic characteristics of vibration dampers under strong wind and large impact loads. Summary of the Invention

[0004] To overcome the shortcomings of the prior art, the present invention proposes a pre-stressed vibration damper, comprising:

[0005] 1. Intermittent steel strand, 3. Assembled integral hammer head and anchoring clamp;

[0006] The gap-shaped steel strand 1 comprises, from the inside out, a central layer circular wire 13, an intermediate layer shaped wire 12, and an outer layer circular wire 11; a gap 14 is provided between the central layer circular wire 13 and the intermediate layer shaped wire 12, and the gap 14 is filled with grease; and the lengths of the intermediate layer shaped wire 12 and the outer layer circular wire 11 are shorter than the central layer circular wire 13; the intermediate layer shaped wire 12 has an arch structure;

[0007] The two ends of the central layer circular line 13 are respectively connected to an integrally assembled hammer head 3. The middle position of each integrally assembled hammer head 3 away from the central layer circular line 13 is a hollow part, and the anchoring clamp is assembled in the hollow part.

[0008] The anchoring clamp is used to hold the central layer circular wire 13 after the target stress is pre-applied by an external tensioning tool; the gap-shaped steel strand 1 and the assembled integral hammer head 3 are coupled and connected through the central layer circular wire 13 after the target stress is pre-applied.

[0009] Optionally, a central hole is provided at one end of the integrally assembled hammerhead 3 near the central layer circle line 13;

[0010] The two ends of the central layer circular line 13 pass through the central hole of the integrally assembled hammer head 3 at one end, and the anchoring clamp is held on the central layer circular line 13 after the pre-applied target stress passes through the central hole.

[0011] The gap-shaped steel strand 1, through the central layer circular wire 13 held by the anchoring clamp and passing through the central hole, is coupled to the integrally assembled hammer head 3 with the internal anchoring clamp.

[0012] Optionally, the vibration damper also includes a wire clamp 2, one end of which is clamped in the middle of the outer circular wire 11, and the other end is sleeved on the external conductor; the assembled integral hammer head 3 is symmetrically distributed on both sides of the wire clamp 2.

[0013] Optionally, the assembled integral hammer head 3 includes a concave hammer head 23 and a convex hammer head 31. The concave hammer head 23 is recessed inward at one end opposite to the offline clamp 2 and closely fits the structure of the convex hammer head 31 protruding outward. The convex hammer head 31 is hollow at one end opposite to the concave hammer head 23, and the opening direction is opposite to the concave hammer head 23. The anchoring clamp is assembled in the hollow part of the convex hammer head 31.

[0014] The central hole includes a first central hole 22 opened in the concave hammer head and a second central hole 33 opened in the convex hammer head 31; the central layer circular line 13 passes through the first central hole 22 and the second central hole 33 in sequence.

[0015] Optionally, the diameters of the first central hole 22 and the second central hole 33 are smaller than the diameter of the gap-shaped steel strand 1 and larger than the diameter of the central layer circular wire 13.

[0016] Optionally, the concave hammer head 23 has a U-shaped structure at one end near the wire clamp 2, with the opening of the U-shaped structure facing the wire clamp 2. A steel sleeve 21 is fixedly installed in the concave part of the opening of the U-shaped structure, and the steel sleeve 21 is sleeved on the outside of the outer round wire 11.

[0017] Optionally, an anchoring clamp embedding groove 32 is provided on the upper and lower edges of the hollow part of the convex hammer head 31. The anchoring clamp embedding groove 32 is closely attached to the second central hole 33, and the anchoring clamp is assembled in the anchoring clamp embedding groove 32.

[0018] Optionally, the anchoring clamp includes an upper clamping piece 41 and a lower clamping piece 42, both of which are wedge-shaped structures. The upper clamping piece 41 is engaged with the anchoring clamp embedding groove 32 provided on the upper edge, and the lower clamping piece 42 is engaged with the anchoring clamp embedding groove 32 provided on the lower edge. After engagement, the wedge-shaped structures of the upper clamping piece 41 and the lower clamping piece 42 face each other sideways, and the upper clamping piece 41 and the lower clamping piece 42 clamp the central layer circular line 13.

[0019] Optionally, the intermediate layer profile 12 includes:

[0020] Multiple profiled lines, the cross-section of which is a quadrilateral with a wider top and a narrower bottom, are twisted and extruded in the same direction around the central layer circular line 13 to form an arch structure.

[0021] This invention also proposes a method for determining the prestress of the anti-vibration hammer steel strand, comprising:

[0022] Dynamic tests were conducted on the unstressed vibration damper steel strand to obtain the first dynamic bending stiffness of the vibration damper steel strand under impact load.

[0023] Dynamic tests were conducted on the prestressed vibration damper steel strand to obtain the second dynamic bending stiffness of the vibration damper steel strand under impact load.

[0024] Based on the ratio of the first dynamic bending stiffness and the second dynamic bending stiffness of the vibration damper steel strand under the impact load, the value of the prestress is adjusted to obtain the target stress of the vibration damper steel strand.

[0025] The anti-vibration hammer steel strand is the intermittent type steel strand of the aforementioned anti-vibration hammer.

[0026] Optionally, the step of adjusting the prestress value to obtain the target stress of the vibration damper steel strand based on the ratio of the first dynamic bending stiffness and the second dynamic bending stiffness of the vibration damper steel strand under the impact load includes:

[0027] If, under the same impact load, the ratio of the first dynamic bending stiffness and the second dynamic bending stiffness of the vibration damper steel strand is within the preset stiffness ratio range, then the value of the prestress will be taken as the target stress of the vibration damper steel strand.

[0028] If, under the same impact load, the ratio of the first dynamic bending stiffness and the second dynamic bending stiffness of the vibration damper steel strand is not within the preset stiffness ratio range, then the prestress is adjusted, and the second dynamic bending stiffness of the prestressed vibration damper steel strand is recalculated until the ratio of the first dynamic bending stiffness and the second dynamic bending stiffness is within the stiffness ratio range. Then, the value of the prestress at this time is taken as the target stress of the vibration damper steel strand.

[0029] Optionally, the dynamic testing of the unstressed vibration damper steel strand to obtain the first dynamic bending stiffness of the vibration damper steel strand under impact load includes:

[0030] The static bending stiffness of the vibration damper steel strand is obtained by using the weight of the weight applied to one end of the vibration damper steel strand and the deflection of the vibration damper steel strand.

[0031] The damping ratio of the vibration damping hammer steel strand is obtained by applying an impact load to one end of the vibration damping hammer steel strand connected to the hammer head and generating damped vibration.

[0032] The vibration signal of the anti-vibration hammer steel strand after applying an impact load was processed by a data acquisition and analysis instrument to obtain the natural frequency of the anti-vibration hammer steel strand.

[0033] By utilizing the static bending stiffness, damping ratio, natural frequency, and excitation frequency of the vibration damper steel strand under impact load, and combining the dynamic bending stiffness calculation formula of the vibration damper steel strand, the first dynamic bending stiffness of the vibration damper steel strand under the impact load is obtained.

[0034] Optionally, the step of obtaining the static bending stiffness of the vibration damper steel strand by utilizing the weight of the weight applied to one end of the vibration damper steel strand and the deflection of the vibration damper steel strand includes:

[0035] The weight of the weight at the yield critical point of the vibration damper steel strand and the deflection of the vibration damper steel strand at this point are obtained by using strain gauges and recorded as the maximum deflection.

[0036] The static bending stiffness of the vibration damper steel strand is obtained by combining the weight of the weights and the maximum deflection with the formula for calculating static bending stiffness.

[0037] Optionally, the formula for calculating the static bending stiffness is:

[0038]

[0039] Where, k represents the static bending stiffness of the vibration damper steel strand; F represents the load at the free end of the vibration damper steel strand, i.e., the weight of the weights connected to the vibration damper steel strand; l represents the distance from the midpoint of the vibration damper steel strand to the connection point between the vibration damper steel strand and the hammer head; h max This indicates the maximum deflection.

[0040] Optionally, obtaining the damping ratio of the vibration damper steel strand by applying an impact load to one end of the vibration damper steel strand connected to the hammer head and generating damped vibration includes:

[0041] An impact load is applied to one end of the anti-vibration hammer steel strand connected to the hammer head, and the vibration attenuation curve of the anti-vibration hammer steel strand generated attenuated vibration is obtained.

[0042] The damping ratio of the anti-vibration hammer steel strand is obtained by combining the amplitude values ​​of two different vibration periods in the vibration attenuation curve with the damping ratio calculation formula.

[0043] Optionally, the damping ratio is calculated as follows:

[0044]

[0045] Where ζ represents the damping ratio of the vibration damper steel strand; b represents the interval period between two vibration cycles; a represents the a-th vibration cycle; u a This represents the amplitude value of the a-th vibration cycle in the vibration decay curve of the vibration damper steel strand; u a+b This represents the amplitude value of the (a+b)th vibration cycle in the vibration attenuation curve of the anti-vibration hammer steel strand.

[0046] Optionally, the method of using the static bending stiffness, damping ratio, natural frequency, and excitation frequency of the vibration damper steel strand under impact load, combined with the dynamic bending stiffness calculation formula of the vibration damper steel strand, to obtain the first dynamic bending stiffness of the vibration damper steel strand under impact load includes:

[0047] The damping of the vibration damper steel strand is calculated by using the mass, damping ratio, and natural frequency of the vibration damper steel strand, combined with the damping calculation formula.

[0048] By utilizing the static bending stiffness, damping, and excitation frequency of the anti-vibration hammer steel strand under impact load, and combining the dynamic bending stiffness calculation formula, the first dynamic bending stiffness of the anti-vibration hammer steel strand under the impact load is calculated.

[0049] Optionally, the formula for calculating the dynamic bending stiffness is:

[0050]

[0051] Where, k d ω represents the dynamic bending stiffness of the vibration damper steel strand; k represents the static bending stiffness of the vibration damper steel strand; m represents the mass of the vibration damper steel strand; ω represents the excitation frequency of the vibration damper steel strand; and c represents the damping of the vibration damper steel strand.

[0052] Based on the same inventive concept, the present invention also provides a system for determining the prestress of anti-vibration hammer steel strand, comprising:

[0053] First dynamic bending stiffness determination module: used to perform dynamic tests on the unstressed anti-vibration hammer steel strand to obtain the first dynamic bending stiffness of the anti-vibration hammer steel strand under impact load;

[0054] Second dynamic bending stiffness determination module: used to perform dynamic testing on the prestressed anti-vibration hammer steel strand to obtain the second dynamic bending stiffness of the anti-vibration hammer steel strand under impact load;

[0055] Target stress determination module: used to adjust the value of the prestress to obtain the target stress of the vibration damper steel strand based on the ratio of the first dynamic bending stiffness and the second dynamic bending stiffness of the vibration damper steel strand under the impact load.

[0056] The anti-vibration hammer steel strand is the intermittent type steel strand of the aforementioned anti-vibration hammer.

[0057] Optionally, the target stress determination module is specifically used for:

[0058] If, under the same impact load, the ratio of the first dynamic bending stiffness and the second dynamic bending stiffness of the vibration damper steel strand is within the preset stiffness ratio range, then the value of the prestress will be taken as the target stress of the vibration damper steel strand.

[0059] If, under the same impact load, the ratio of the first dynamic bending stiffness and the second dynamic bending stiffness of the vibration damper steel strand is not within the preset stiffness ratio range, then the prestress is adjusted, and the second dynamic bending stiffness of the prestressed vibration damper steel strand is recalculated until the ratio of the first dynamic bending stiffness and the second dynamic bending stiffness is within the stiffness ratio range. Then, the value of the prestress at this time is taken as the target stress of the vibration damper steel strand.

[0060] Optionally, the first dynamic bending stiffness determination module is specifically used for:

[0061] The static bending stiffness of the vibration damper steel strand is obtained by using the weight of the weight applied to one end of the vibration damper steel strand and the deflection of the vibration damper steel strand.

[0062] The damping ratio of the vibration damping hammer steel strand is obtained by applying an impact load to one end of the vibration damping hammer steel strand connected to the hammer head and generating damped vibration.

[0063] The vibration signal of the anti-vibration hammer steel strand after applying an impact load was processed by a data acquisition and analysis instrument to obtain the natural frequency of the anti-vibration hammer steel strand.

[0064] By utilizing the static bending stiffness, damping ratio, natural frequency, and excitation frequency of the vibration damper steel strand under impact load, and combining the dynamic bending stiffness calculation formula of the vibration damper steel strand, the first dynamic bending stiffness of the vibration damper steel strand under the impact load is obtained.

[0065] Optionally, the first dynamic bending stiffness determination module obtains the static bending stiffness of the vibration damper steel strand using the weight of the weight applied to one end of the vibration damper steel strand and the deflection of the vibration damper steel strand, including:

[0066] The weight of the weight at the yield critical point of the vibration damper steel strand and the deflection of the vibration damper steel strand at this point are obtained by using strain gauges and recorded as the maximum deflection.

[0067] The static bending stiffness of the vibration damper steel strand is obtained by combining the weight of the weights and the maximum deflection with the formula for calculating static bending stiffness.

[0068] Optionally, the formula for calculating the static bending stiffness in the first dynamic bending stiffness determination module is:

[0069]

[0070] Where, k represents the static bending stiffness of the vibration damper steel strand; F represents the load at the free end of the vibration damper steel strand, i.e., the weight of the weights connected to the vibration damper steel strand; l represents the distance from the midpoint of the vibration damper steel strand to the connection point between the vibration damper steel strand and the hammer head; h max This indicates the maximum deflection.

[0071] Optionally, the first dynamic bending stiffness determination module obtains the damping ratio of the vibration damper steel strand by applying an impact load to one end of the vibration damper steel strand connected to the hammer head, resulting in damped vibration, including:

[0072] An impact load is applied to one end of the anti-vibration hammer steel strand connected to the hammer head, and the vibration attenuation curve of the anti-vibration hammer steel strand generated attenuated vibration is obtained.

[0073] The damping ratio of the anti-vibration hammer steel strand is obtained by combining the amplitude values ​​of two different vibration periods in the vibration attenuation curve with the damping ratio calculation formula.

[0074] Optionally, the damping ratio calculation formula in the first dynamic bending stiffness determination module is:

[0075]

[0076] Where ζ represents the damping ratio of the vibration damper steel strand; b represents the interval period between two vibration cycles; a represents the a-th vibration cycle; u a This represents the amplitude value of the a-th vibration cycle in the vibration decay curve of the vibration damper steel strand; u a+b This represents the amplitude value of the (a+b)th vibration cycle in the vibration attenuation curve of the anti-vibration hammer steel strand.

[0077] Optionally, the first dynamic bending stiffness determination module utilizes the static bending stiffness, damping ratio, natural frequency, and excitation frequency of the vibration damper steel strand under impact load, combined with the dynamic bending stiffness calculation formula of the vibration damper steel strand, to obtain the first dynamic bending stiffness of the vibration damper steel strand under impact load, including:

[0078] The damping of the vibration damper steel strand is calculated by using the mass, damping ratio, and natural frequency of the vibration damper steel strand, combined with the damping calculation formula.

[0079] By utilizing the static bending stiffness, damping, and excitation frequency of the anti-vibration hammer steel strand under impact load, and combining the dynamic bending stiffness calculation formula, the first dynamic bending stiffness of the anti-vibration hammer steel strand under the impact load is calculated.

[0080] Optionally, the dynamic bending stiffness calculation formula in the first dynamic bending stiffness determination module is:

[0081]

[0082] Where, k d ω represents the dynamic bending stiffness of the vibration damper steel strand; k represents the static bending stiffness of the vibration damper steel strand; m represents the mass of the vibration damper steel strand; ω represents the excitation frequency of the vibration damper steel strand; and c represents the damping of the vibration damper steel strand.

[0083] Based on the same inventive concept, the present invention also provides a computer device, comprising: one or more processors;

[0084] Memory, used to store one or more programs;

[0085] When the one or more programs are executed by the one or more processors, a method for determining the prestress of anti-vibration hammer steel strands as described above is implemented.

[0086] Based on the same inventive concept, the present invention also provides a computer-readable storage medium having a computer program stored thereon, wherein when the computer program is executed, it implements the method for determining the prestress of the anti-vibration hammer steel strand as described above.

[0087] Compared with the closest existing technology, the present invention has the following beneficial effects:

[0088] This invention provides a prestressed vibration damper, comprising: a gap-shaped steel strand, an integrally assembled hammer head, and an anchoring clamp; the gap-shaped steel strand comprises, from the inside out, a central layer circular wire, an intermediate layer circular wire, and an outer layer circular wire; a gap is provided between the central layer circular wire and the intermediate layer circular wire, the gap being filled with grease, and the lengths of the intermediate layer circular wire and the outer layer circular wire are shorter than the central layer circular wire; the intermediate layer circular wire has an arched structure; an integrally assembled hammer head is connected to each end of the central layer circular wire, and the middle position of each integrally assembled hammer head away from the central layer circular wire is a hollow portion, with the anchoring clamp assembled in the hollow portion; the anchoring clamp is used for external tensioning. The central layer circular wire, after being prestressed with a target stress, is clamped. This invention, by prestressing the central layer circular wire, compresses the outer layer circular wire and the intermediate layer profile. The tensile stress generated under vertical impact load first offsets the compressive stress of the outer and intermediate layer profiles, thereby reducing the tensile stress of the outer and intermediate layer profiles of the steel strand. This increases the bending stiffness of the gap-shaped steel strand and improves its vibration damping effect. The intermediate layer profiles form an arch structure, which increases the moment of inertia about the center and changes the contact between strands from line-to-line to surface-to-surface, resulting in more uniform stress distribution between strands and avoiding stress concentration as seen in the contact between circular wire strands, thus enhancing bending stiffness.

[0089] Furthermore, the prestressed vibration damper of the present invention has a gap between the central layer circular wire and the intermediate layer profile wire, and the gap is filled with grease. This structural measure is used to reduce the frictional resistance between the central layer circular wire and the intermediate layer profile wire, facilitate the application of prestress to the central layer circular wire, reduce the wear between the central layer circular wire and the intermediate layer profile wire, reduce the probability of strand breakage, and extend the service life of the gap-shaped steel strand.

[0090] Unlike traditional vibration damping hammers that use a crimped connection between the steel strand and the hammer head, the prestressed vibration damping hammer achieves its connection through the coupling between the gapped steel strand and the integrally assembled hammer head (i.e., by using anchoring clamps within the integrally assembled hammer head to hold the prestressed center layer of the steel strand). The anchoring clamps within the integrally assembled hammer head hold the prestressed center layer of the steel strand, thereby increasing the stiffness of the steel strand. Simultaneously, by holding the prestressed center layer of the steel strand with the anchoring clamps, the integrally assembled hammer head with its built-in anchoring clamps is fixed to both ends of the gapped steel strand.

[0091] A method and system for determining the prestress of vibration damper steel strand includes: performing dynamic testing on unstressed vibration damper steel strand to obtain the first dynamic bending stiffness of the vibration damper steel strand under impact load; performing dynamic testing on prestressed vibration damper steel strand to obtain the second dynamic bending stiffness of the vibration damper steel strand under impact load; and adjusting the prestress value based on the ratio of the first dynamic bending stiffness and the second dynamic bending stiffness of the vibration damper steel strand under the impact load to obtain the target stress of the vibration damper steel strand. This achieves the testing of the dynamic characteristics of the vibration damper steel strand under large impact load and the selection of the prestress of the steel strand. Attached Figure Description

[0092] Figure 1 A partial structural cross-sectional view of a prestressed vibration damper provided for this invention;

[0093] Figure 2 A top view of the structure of a prestressed vibration damper provided by the present invention;

[0094] Figure 3 This is a schematic diagram of the cross-section of a gap-type steel strand;

[0095] Figure 4 A schematic diagram of the stress on a pre-tensioned gap steel strand;

[0096] Figure 5 This is a schematic diagram of the structure of a concave hammerhead;

[0097] Figure 6 This is a schematic diagram of the structure of a convex hammerhead;

[0098] Figure 7This is a schematic diagram of the anchoring clamp structure;

[0099] Figure 8 A schematic diagram of the structure of the gap-type steel strand near the end of the assembled integral hammerhead;

[0100] Figure 9 A flowchart illustrating a method for determining the prestress of a vibration damper steel strand provided by the present invention;

[0101] Figure 10 This is a schematic diagram of the dynamic testing model;

[0102] Figure 11 The vibration attenuation curve of the steel strand;

[0103] Figure 12 A flowchart illustrating the process of adjusting prestress;

[0104] Figure 13 A schematic diagram of the structure of a system for determining the prestress of a vibration damper steel strand provided by the present invention;

[0105] Among them, 1-gap steel strand, 2-wire clamp, 3-assembled integral hammer head, 11-outer layer round wire, 12-middle layer wire, 13-center layer round wire, 14-gap, 21-steel sleeve, 22-first center hole, 23-concave hammer head, 31-convex hammer head, 32-anchoring clamp embedding groove, 33-second center hole, 41-upper clamping piece, 42-lower clamping piece, 43-third center hole. Detailed Implementation

[0106] The specific embodiments of the present invention will be further described in detail below with reference to the accompanying drawings.

[0107] Example 1:

[0108] This invention provides a prestressed vibration damper, such as... Figure 1 and Figure 2 As shown, it includes: a gap-shaped steel strand 1, an integrally assembled hammer head 3, and an anchoring clamp; the gap-shaped steel strand 1 includes, from the inside out, a central layer circular wire 13, an intermediate layer profiled wire 12, and an outer layer circular wire 11, with a gap 14 between the central layer circular wire 13 and the intermediate layer profiled wire 12, and the gap 14 is filled with grease; and the lengths of the intermediate layer profiled wire 12 and the outer layer circular wire 11 are shorter than the central layer circular wire 13; as shown... Figure 3The intermediate layer profile 12 shown is an arch structure; each end of the central layer circular line 13 is connected to an integrally assembled hammer head 3, and the middle position of each integrally assembled hammer head 3 away from the end of the central layer circular line 13 is a hollow part, and the anchoring clamp is assembled in the hollow part; the anchoring clamp is used to clamp the central layer circular line 13 after the target stress is pre-applied by an external tensioning tool; the gap-shaped steel strand 1 and the integrally assembled hammer head 3 are coupled and connected through the central layer circular line 13 after the target stress is pre-applied.

[0109] like Figure 4 As shown, applying pre-tension to the central layer circular wire 13 causes a redistribution of stress in the steel strand. Since the outer strands and the middle layer profile 12 are stranded, their stress and deformation are consistent. Therefore, while the central layer circular wire 13 is under tension, the outer layer circular wire 11 and the middle layer profile 12 are under compression. The tensile stress generated under vertical impact load first offsets the compressive stress in the outer and middle layer profiles 12, thereby reducing the tensile stress in the outer and middle layer profiles 12 of the steel strand. This increases the bending stiffness of the gap-type steel strand 1, resulting in better vibration damping. Typically, the pre-stress applied to the central layer circular wire 13 is 2%T-5%T, where T is the tensile strength of the steel strand.

[0110] The width of the gap 14 is set to (0.5mm-1mm), and the gap 14 is set between the center layer circular line 13 and the intermediate layer profile 12. The gap 14 is filled with grease to reduce the frictional resistance between the center layer circular line 13 and the intermediate layer profile 12, so as to facilitate the application of prestress to the center layer circular line, reduce the wear between the center layer circular line 13 and the intermediate layer profile 12, thereby reducing the probability of strand breakage and extending the strand life.

[0111] The intermediate layer profile 12 includes multiple profiles, each profile having a cross-section that is wider at the top and narrower at the bottom, and the multiple profiles are twisted and compressed in the same direction around the central layer circular line 13 to form an arch structure.

[0112] The cross-section of the profile can be an approximate quadrilateral, wider at the top and narrower at the bottom. The "wider at the top" refers to the greater width of the profile near the outermost circular wire 11 within the interstitial steel strand 1, while the "narrower at the bottom" refers to the smaller width of the profile near the central circular wire 13 within the interstitial steel strand 1. For example... Figure 3 As shown.

[0113] The arch structure formed by multiple strands in the middle layer increases the moment of inertia about the center and changes the contact between strands from line-to-line to surface-to-surface. Therefore, changing the middle layer strand 12 from a round strand to a shaped strand increases the contact area between strands, making the stress distribution between strands more uniform and avoiding stress concentration as seen in the contact between round strands, thus enhancing bending stiffness. Furthermore, the moment of inertia of the middle layer strand 12 as a shaped strand is greater than that of a round strand, thereby increasing the bending stiffness of the middle layer strand 12. The center layer round strand 13 and the outer layer round strand 11 of the gap-shaped steel strand 1 are round strands.

[0114] Each of the assembled integral hammerheads 3 has a central hole at one end near the central layer circular line 13; both ends of the central layer circular line 13 pass through the central holes of the assembled integral hammerheads 3 at their respective ends, and the anchoring clamp is held on the central layer circular line 13 after pre-applied target stress through the central hole; the gap-shaped steel strand 1 is coupled to the assembled integral hammerhead 3 with the internal anchoring clamp through the central layer circular line 13 held by the anchoring clamp and passing through the central hole.

[0115] The central layer circular line 13 passing through the central hole is the central layer circular line 13 after the outer layer circular line 11 and the middle layer circular line 12 are stripped from the gap-shaped steel strand 1. The lengths of the middle layer circular line 12 and the outer layer circular line 11 are shorter than the central layer circular line 13 because an external tensioning tool is needed to pre-stress the central layer circular line 13.

[0116] The vibration damper also includes a wire clamp 2, one end of which is clamped in the middle of the outer circular wire 11, and the other end is sleeved on the external conductor.

[0117] The clamp 2 connects to the external conductor at one end and to the outer round wire 11 (i.e., the gap-type steel strand 1) at the other end, thus connecting the vibration damper to the external conductor; the assembled integral hammer head 3 is symmetrically distributed on both sides of the clamp 2.

[0118] like Figures 5-6 As shown, the assembled integral hammer head 3 includes a concave hammer head 23 and a convex hammer head 31. The concave hammer head 23 has one end facing away from the line clamp 2 that is recessed inward and closely attached to the structure of the convex hammer head 31 that protrudes outward. The convex hammer head 31 has a hollow opening at one end facing away from the concave hammer head 23, and the opening direction is opposite to the concave hammer head 23. The anchoring clamp is assembled on the hollow part of the convex hammer head 31. The central hole includes a first central hole 22 opened in the concave hammer head 23 and a second central hole 33 opened in the convex hammer head 31. The central layer circular line 13 passes through the first central hole 22 and the second central hole 33 in sequence.

[0119] The central layer circular wire 13 passes through the first central hole 22 and the second central hole 33 in sequence and enters the interior of the anchoring clamp. The central layer circular wire 13 is prestressed by the tensioning tool and the anchoring clamp holds the prestressed central layer circular wire 13. The length of the central layer circular wire 13 after the outer layer circular wire 11 and the middle layer wire 12 are stripped from the gap-shaped steel strand 1 is equal to the axial length of the convex hammer head.

[0120] The diameters of the first central hole 22 and the second central hole 33 are smaller than the diameter of the gap-shaped steel strand 1, but larger than the diameter of the central layer circular wire 13.

[0121] After the outer layer round wire 11 and the middle layer wire 12 are stripped from the gap-shaped steel strand 1, the center layer round wire 13 passes through the first center hole 22. The outer layer round wire 11 and the middle layer wire 12 abut against the first center hole 22, ensuring that the center layer round wire 13 does not move significantly when the tensioning tool applies prestress to the center layer round wire 13, and enabling the convex hammer head 31 and the concave hammer head 23 to be more tightly combined into a smooth whole.

[0122] The concave hammer head 23 has a U-shaped structure at one end near the wire clamp 2, with the opening of the U-shaped structure facing the wire clamp 2. A steel sleeve 21 is fixedly installed in the concave part of the opening of the U-shaped structure, and the steel sleeve 21 is sleeved on the outside of the outer round wire 11.

[0123] An anchoring clamp embedding groove 32 is provided on the upper and lower edges of the hollow part of the convex hammer head 31. The anchoring clamp embedding groove 32 is closely attached to the second central hole 33, and the anchoring clamp is assembled in the anchoring clamp embedding groove 32.

[0124] like Figure 7 As shown, the anchoring clamp includes an upper clamping piece 41 and a lower clamping piece 42. Both the upper clamping piece 41 and the lower clamping piece 42 are wedge-shaped structures. The upper clamping piece 41 is engaged with the anchoring clamp embedding groove 32 provided on the upper edge, and the lower clamping piece 42 is engaged with the anchoring clamp embedding groove 32 provided on the lower edge. After being engaged, the wedge-shaped structures of the upper clamping piece 41 and the lower clamping piece 42 face each other with their sides, forming a space for the central layer circular line 13 to pass through, which can be called the third central hole. The central layer circular line 13 is clamped between the upper clamping piece 41 and the lower clamping piece 42.

[0125] When using the anchoring clamp assembled within the integral hammer head 3 to clamp the center layer circular wire 13 of the gap-shaped steel strand 1, such as Figure 8As shown, the interstitial steel strand 1 is peeled to obtain the central layer circular wire 13. The interstitial steel strand 1 is inserted into the steel tube sleeve of the concave hammer head 23. The outer layer circular wire 11 and the middle layer wire 12 abut against the first central hole 22 of the concave hammer head 23. The central layer circular wire 13 passes through the first and second central holes in sequence and enters the second central hole 33. Then, the prestressed central layer circular wire 13 is clamped by the upper clamping plate 41 and the lower clamping plate 42 of the anchoring clamp.

[0126] After the central layer circular wire 13 is prestressed and clamped, the tensile stress generated under the vertical impact load first offsets the compressive stress of the outer and middle layer profiles 12, thereby reducing the tensile stress of the outer and middle layer profiles 12 of the steel strand. The bending stiffness of the gap steel strand 1 increases, and the vibration damping effect is better.

[0127] Unlike traditional vibration damping hammers that use a crimping connection between the steel strand and the hammer head, the prestressed vibration damping hammer achieves its connection through the coupling between the intermittent steel strand 1 and the integrally assembled hammer head 3 (i.e., by using anchoring clamps within the integrally assembled hammer head 3 to hold the prestressed intermittent steel strand 1's central layer circular wire 13). The anchoring clamps within the integrally assembled hammer head 3 hold the prestressed central layer circular wire 13, thereby increasing the stiffness of the steel strand. Simultaneously, by holding the prestressed central layer circular wire 13 with the anchoring clamps, the integrally assembled hammer head 3 with its built-in anchoring clamps is fixed to both ends of the intermittent steel strand 1.

[0128] Example 2

[0129] This invention provides a method for determining the prestress of the steel strand in a vibration damper, used to determine the value of the prestress for a prestressed vibration damper as described in Example 1. Figure 9 As shown, it includes:

[0130] S1. Perform dynamic tests on the unstressed anti-vibration hammer steel strand to obtain the first dynamic bending stiffness of the anti-vibration hammer steel strand under impact load.

[0131] S2. Perform dynamic tests on the prestressed anti-vibration hammer steel strand to obtain the second dynamic bending stiffness of the anti-vibration hammer steel strand under impact load.

[0132] S3. Based on the ratio of the first dynamic bending stiffness and the second dynamic bending stiffness of the vibration damper steel strand under the impact load, adjust the value of the prestress to obtain the target stress of the vibration damper steel strand.

[0133] The anti-vibration hammer steel strand is the gap-type steel strand of the anti-vibration hammer in Example 1.

[0134] The dynamic test of the anti-vibration hammer steel strand before and after prestressing can be performed by testing the same anti-vibration hammer steel strand before and after prestressing, or by selecting two anti-vibration hammer steel strands of the same specification before and after prestressing.

[0135] In step S1, a dynamic test is performed on the unstressed vibration damper steel strand to obtain the first dynamic bending stiffness of the vibration damper steel strand under impact load, specifically including:

[0136] S11. The static bending stiffness of the anti-vibration hammer steel strand is obtained by using the weight of the weight applied to one end of the anti-vibration hammer steel strand and the deflection of the anti-vibration hammer steel strand.

[0137] Specifically, strain gauges are used to obtain the weight of the weight at the yield critical point of the vibration damper steel strand and the deflection of the vibration damper steel strand at this point, which is recorded as the maximum deflection.

[0138] Optionally, utilize, such as Figure 10 The dynamic test model shown obtains the maximum deflection at the yield critical point of the vibration damper steel strand. The test model includes strain gauges, an accelerometer, and weights. The vibration damper steel strand clamp 2 is held in the test model. The strain gauge is attached to the position of the vibration damper steel strand connecting clamp 2. The accelerometer is connected to one end of the vibration damper steel strand connecting hammer head. The weight is connected to one end of the vibration damper steel strand connecting hammer head. The weight is added according to the test requirements. In this embodiment, the weight is gradually increased at one end of the vibration damper steel strand connecting hammer head. The strain gauge is used to obtain the yield critical point of the vibration damper steel strand, thereby obtaining the maximum deflection.

[0139] The static bending stiffness of the vibration damper steel strand is obtained by combining the weight of the weights and the maximum deflection with the formula for calculating static bending stiffness.

[0140] The static bending stiffness of the vibration damper steel strand is calculated using the deflection curve equation, which is:

[0141]

[0142] Where h(x) represents the deflection of the vibration damper strand at position x, where x represents the position of the vibration damper strand, which is 0 at the midpoint of the vibration damper strand (i.e., the connection between the vibration damper strand and the clamp) and l at the connection between the vibration damper strand and the hammer head; k represents the static bending stiffness of the vibration damper strand; F represents the load at the free end of the vibration damper strand; and l represents the distance from the midpoint of the vibration damper strand to the connection between the vibration damper strand and the hammer head. According to this formula, the deflection is greatest at the connection between the vibration damper strand and the hammer head, and the maximum deflection is:

[0143]

[0144] The formula for calculating the static bending stiffness of the vibration damper steel strand is obtained by conversion using this formula. The formula for calculating the static bending stiffness is:

[0145]

[0146] Where, k represents the static bending stiffness of the vibration damper steel strand; F represents the load at the free end of the vibration damper steel strand, i.e., the weight of the weights connected to the vibration damper steel strand; l represents the distance from the midpoint of the vibration damper steel strand to the connection point between the vibration damper steel strand and the hammer head; h max This indicates the maximum deflection.

[0147] S12. The damping ratio of the anti-vibration hammer steel strand is obtained by applying an impact load to one end of the anti-vibration hammer steel strand connected to the hammer head and generating damped vibration.

[0148] Specifically, an impact load is applied to one end of the vibration damping hammer steel strand connected to the hammer head, and the vibration decay curve of the damped vibration generated by the vibration damping hammer steel strand is obtained. A load is applied to one end of the vibration damping hammer steel strand connected to the hammer head to produce a certain initial displacement, and then unloaded, causing the vibration damping hammer steel strand to produce free decaying vibration. The vibration decay curve of the decaying vibration generated after unloading the vibration damping hammer steel strand is recorded, such as... Figure 11 As shown, TD represents one vibration cycle, u1 represents the first vibration cycle, and u i U represents the i-th oscillation period. i+1 Let represent the (i+1)th vibration cycle. Based on the amplitude values ​​of two different vibration cycles in the vibration decay curve, and combined with the damping ratio calculation formula, the damping ratio of the vibration damper steel strand is obtained. The damping ratio calculation formula is:

[0149]

[0150] Where ζ represents the damping ratio of the vibration damper steel strand; b represents the interval period between two vibration cycles; a represents the a-th vibration cycle; u a This represents the amplitude value of the a-th vibration cycle in the vibration decay curve of the vibration damper steel strand; u a+b This represents the amplitude value of the (a+b)th vibration cycle in the vibration attenuation curve of the anti-vibration hammer steel strand.

[0151] S13. The vibration signal of the anti-vibration hammer steel strand after the impact load is applied is processed by a data acquisition and analysis instrument to obtain the natural frequency of the anti-vibration hammer steel strand.

[0152] Specifically, the natural frequency of the vibration damper steel strand can be measured using the autospectral analysis method. The test steps are as follows: place the accelerometer at one end of the vibration damper steel strand, connect the output signal to the vibration test channel, turn on the power of the test instrument, enter the DAS2003 data acquisition and analysis software, set various operating parameters, select the single frequency response analysis function, and obtain the natural frequency of the vibration damper steel strand.

[0153] S14. Using the static bending stiffness, damping ratio, natural frequency, and excitation frequency of the anti-vibration hammer steel strand under impact load, combined with the dynamic bending stiffness calculation formula of the anti-vibration hammer steel strand, the first dynamic bending stiffness of the anti-vibration hammer steel strand under the impact load is obtained.

[0154] Specifically, S141, using the mass, damping ratio, and natural frequency of the vibration damper steel strand, and combining this with the damping calculation formula, the damping of the vibration damper steel strand is calculated; the damping calculation formula for the vibration damper steel strand is:

[0155] c = 2mw n ζ

[0156] Where c represents the damping of the vibration damper steel strand; ζ represents the damping ratio of the vibration damper steel strand; w n represents the natural frequency of the vibration damper steel strand; m represents the mass of the vibration damper steel strand.

[0157] S142. Using the static bending stiffness, damping, and excitation frequency of the anti-vibration hammer steel strand under impact load, combined with the dynamic bending stiffness calculation formula, the first dynamic bending stiffness of the anti-vibration hammer steel strand under the impact load is calculated.

[0158] Specifically, the formula for calculating dynamic bending stiffness is:

[0159]

[0160] Where, k d The dynamic bending stiffness of the vibration damper steel strand is represented by ω, and the static bending stiffness is represented by k. The mass of the vibration damper steel strand is represented by m. ω represents the excitation frequency of the vibration damper steel strand, which is collected using excitation equipment under different impact loads. c represents the damping of the vibration damper steel strand, f is the impact force, i.e., the impact load on the vibration damper steel strand. y represents the displacement response of the vibration damper steel strand under impact load, i.e., the displacement of the end of the vibration damper steel strand near the hammer head. j refers to the imaginary part of the dynamic bending stiffness of the vibration damper steel strand.

[0161] From the formula for calculating dynamic bending stiffness, it can be seen that dynamic bending stiffness is related to the excitation frequency and changes with the excitation frequency, rather than being a fixed value. Transforming this formula yields the following formula for calculating dynamic bending stiffness:

[0162]

[0163] Where, k d Let represent the dynamic bending stiffness of the vibration damper steel strand, k represent the static bending stiffness of the vibration damper steel strand, m represent the mass of the vibration damper steel strand, ω represent the excitation frequency of the vibration damper steel strand, and c represent the damping of the vibration damper steel strand. When the excitation frequency is 0, the dynamic bending stiffness is equal to the static bending stiffness, so static stiffness is a special case of dynamic stiffness.

[0164] The calculation formula shows that the dynamic bending stiffness is related not only to the static bending stiffness and excitation frequency of the vibration damper steel strand, but also to the mass and damping of the vibration damper steel strand. Therefore, when the dynamic bending stiffness of the vibration damper is insufficient in a certain frequency range and needs to be optimized, it can be optimized in a targeted manner by increasing the static bending stiffness, adjusting the mass, increasing the damping, and changing the excitation frequency, thereby improving the dynamic bending stiffness.

[0165] In step S2, a dynamic test is performed on the prestressed anti-vibration hammer steel strand to obtain the second dynamic bending stiffness of the anti-vibration hammer steel strand under impact load.

[0166] Using the method obtained in step S1 to determine the first dynamic bending stiffness of the vibration damper steel strand under impact load, the second dynamic bending stiffness of the prestressed vibration damper steel strand under impact load is obtained.

[0167] The static bending stiffness of the prestressed vibration damper steel strand is obtained by using the weight of the weight applied to one end of the prestressed vibration damper steel strand and the deflection of the vibration damper steel strand.

[0168] The damping ratio of the prestressed vibration damping hammer steel strand was obtained by applying an impact load to one end of the prestressed vibration damping hammer steel strand connected to the hammer head and generating damped vibration.

[0169] The vibration signal of the anti-vibration hammer steel strand after applying impact load was processed by a data acquisition and analysis instrument to obtain the natural frequency of the anti-vibration hammer steel strand after prestressing.

[0170] By utilizing the static bending stiffness, damping ratio, natural frequency, and excitation frequency of the prestressed vibration damper steel strand under impact load, and combining the dynamic bending stiffness calculation formula of the vibration damper steel strand, the second dynamic bending stiffness of the prestressed vibration damper steel strand under the impact load is obtained.

[0171] In step S3, based on the ratio of the first dynamic bending stiffness and the second dynamic bending stiffness of the vibration damper steel strand under the impact load, the value of the prestress is adjusted to obtain the target stress of the vibration damper steel strand.

[0172] Specifically, such as Figure 12As shown, if the ratio of the first dynamic bending stiffness and the second dynamic bending stiffness of the vibration damper steel strand is within the preset stiffness ratio range under the same impact load, then the value of the prestress will be taken as the target stress of the vibration damper steel strand.

[0173] If, under the same impact load, the ratio of the first dynamic bending stiffness and the second dynamic bending stiffness of the vibration damper steel strand is not within the preset stiffness ratio range, then the prestress is adjusted, and the second dynamic bending stiffness of the prestressed vibration damper steel strand is recalculated until the ratio of the first dynamic bending stiffness and the second dynamic bending stiffness is within the stiffness ratio range. Then, the value of the prestress at this time is taken as the target stress of the vibration damper steel strand.

[0174] In this embodiment, the stiffness ratio range is 10% ≤ λ ≤ 30%, where λ represents the ratio of the first dynamic bending stiffness and the second dynamic bending stiffness of the vibration damper steel strand. Figure 12 The applied tension, also known as the prestress mentioned in this embodiment, is the target stress.

[0175] Since the anti-vibration hammer steel strand will lose some of its prestress due to shrinkage after prestressing, using tensioning tools to prestress the anti-vibration hammer steel strand can increase the target stress by 2%-5% and reduce the impact of shrinkage loss.

[0176] The method provided by this invention can test the dynamic bending stiffness and damping coefficient of anti-vibration hammer steel strands under impact loads, realizing the dynamic characteristic testing of anti-vibration hammer steel strands under large impact loads and the selection of prestress for anti-vibration hammer steel strands.

[0177] Example 3

[0178] Based on the same inventive concept, this invention also provides a system for determining the prestress of the steel strand of a vibration damper, used to provide a system for determining the value of the prestress of a prestressed vibration damper as described in Example 1, such as... Figure 13 As shown, it includes:

[0179] First dynamic bending stiffness determination module: used to perform dynamic tests on the unstressed anti-vibration hammer steel strand to obtain the first dynamic bending stiffness of the anti-vibration hammer steel strand under impact load;

[0180] Second dynamic bending stiffness determination module: used to perform dynamic testing on the prestressed anti-vibration hammer steel strand to obtain the second dynamic bending stiffness of the anti-vibration hammer steel strand under impact load;

[0181] Target stress determination module: used to adjust the value of the prestress to obtain the target stress of the vibration damper steel strand based on the ratio of the first dynamic bending stiffness and the second dynamic bending stiffness of the vibration damper steel strand under the impact load.

[0182] The anti-vibration hammer steel strand is the gap-type steel strand of the anti-vibration hammer in Example 1.

[0183] The target stress determination module is specifically used for:

[0184] If, under the same impact load, the ratio of the first dynamic bending stiffness and the second dynamic bending stiffness of the vibration damper steel strand is within the preset stiffness ratio range, then the value of the prestress will be taken as the target stress of the vibration damper steel strand.

[0185] If, under the same impact load, the ratio of the first dynamic bending stiffness and the second dynamic bending stiffness of the vibration damper steel strand is not within the preset stiffness ratio range, then the prestress is adjusted, and the second dynamic bending stiffness of the prestressed vibration damper steel strand is recalculated until the ratio of the first dynamic bending stiffness and the second dynamic bending stiffness is within the stiffness ratio range. Then, the value of the prestress at this time is taken as the target stress of the vibration damper steel strand.

[0186] The first dynamic bending stiffness determination module is specifically used for:

[0187] The static bending stiffness of the vibration damper steel strand is obtained by using the weight of the weight applied to one end of the vibration damper steel strand and the deflection of the vibration damper steel strand.

[0188] The damping ratio of the vibration damping hammer steel strand is obtained by applying an impact load to one end of the vibration damping hammer steel strand connected to the hammer head and generating damped vibration.

[0189] The vibration signal of the anti-vibration hammer steel strand after applying an impact load was processed by a data acquisition and analysis instrument to obtain the natural frequency of the anti-vibration hammer steel strand.

[0190] By utilizing the static bending stiffness, damping ratio, natural frequency, and excitation frequency of the vibration damper steel strand under impact load, and combining the dynamic bending stiffness calculation formula of the vibration damper steel strand, the first dynamic bending stiffness of the vibration damper steel strand under the impact load is obtained.

[0191] The first dynamic bending stiffness determination module uses the weight of the weight applied to one end of the vibration damper steel strand and the deflection of the vibration damper steel strand to obtain the static bending stiffness of the vibration damper steel strand, including:

[0192] The weight of the weight at the yield critical point of the vibration damper steel strand and the deflection of the vibration damper steel strand at this point are obtained by using strain gauges and recorded as the maximum deflection.

[0193] The static bending stiffness of the vibration damper steel strand is obtained by combining the weight of the weights and the maximum deflection with the formula for calculating static bending stiffness.

[0194] The formula for calculating static bending stiffness in the first dynamic bending stiffness determination module is:

[0195]

[0196] Where, k represents the static bending stiffness of the vibration damper steel strand; F represents the load at the free end of the vibration damper steel strand, i.e., the weight of the weights connected to the vibration damper steel strand; l represents the distance from the midpoint of the vibration damper steel strand to the connection point between the vibration damper steel strand and the hammer head; h max This indicates the maximum deflection.

[0197] The first dynamic bending stiffness determination module obtains the damping ratio of the vibration damper steel strand by applying an impact load to one end of the vibration damper steel strand connected to the hammer head, resulting in damped vibration. This includes:

[0198] An impact load is applied to one end of the anti-vibration hammer steel strand connected to the hammer head, and the vibration attenuation curve of the anti-vibration hammer steel strand generated attenuated vibration is obtained.

[0199] The damping ratio of the anti-vibration hammer steel strand is obtained by combining the amplitude values ​​of two different vibration periods in the vibration attenuation curve with the damping ratio calculation formula.

[0200] The formula for calculating the damping ratio in the first dynamic bending stiffness determination module is:

[0201]

[0202] Where ζ represents the damping ratio of the vibration damper steel strand; b represents the interval period between two vibration cycles; a represents the a-th vibration cycle; u a This represents the amplitude value of the a-th vibration cycle in the vibration decay curve of the vibration damper steel strand; u a+b This represents the amplitude value of the (a+b)th vibration cycle in the vibration attenuation curve of the anti-vibration hammer steel strand.

[0203] The first dynamic bending stiffness determination module utilizes the static bending stiffness, damping ratio, natural frequency, and excitation frequency of the vibration damper steel strand under impact load, combined with the dynamic bending stiffness calculation formula of the vibration damper steel strand, to obtain the first dynamic bending stiffness of the vibration damper steel strand under the impact load, including:

[0204] The damping of the vibration damper steel strand is calculated by using the mass, damping ratio, and natural frequency of the vibration damper steel strand, combined with the damping calculation formula.

[0205] By utilizing the static bending stiffness, damping, and excitation frequency of the anti-vibration hammer steel strand under impact load, and combining the dynamic bending stiffness calculation formula, the first dynamic bending stiffness of the anti-vibration hammer steel strand under the impact load is calculated.

[0206] The formula for calculating dynamic bending stiffness in the first dynamic bending stiffness determination module is:

[0207]

[0208] Where, k dω represents the dynamic bending stiffness of the vibration damper steel strand; k represents the static bending stiffness of the vibration damper steel strand; m represents the mass of the vibration damper steel strand; ω represents the excitation frequency of the vibration damper steel strand; and c represents the damping of the vibration damper steel strand.

[0209] Example 4:

[0210] Based on the same inventive concept, this invention also provides a computer device, which includes a processor and a memory. The memory stores a computer program, which includes program instructions. The processor executes the program instructions stored in the computer storage medium. The processor may be a Central Processing Unit (CPU), or other general-purpose processors, digital signal processors (DSPs), application-specific integrated circuits (ASICs), field-programmable gate arrays (FPGAs), or other programmable logic devices, discrete gate or transistor logic devices, discrete hardware components, etc. It is the computing and control core of the terminal, suitable for implementing one or more instructions, specifically suitable for loading and executing one or more instructions in the computer storage medium to implement corresponding method flows or corresponding functions, thereby realizing the steps of the method for determining the prestress of anti-vibration hammer steel strand in the above embodiments.

[0211] Example 5:

[0212] Based on the same inventive concept, this invention also provides a storage medium, specifically a computer-readable storage medium (Memory), which is a memory device in a computer device used to store programs and data. It is understood that the computer-readable storage medium here can include both the built-in storage medium in the computer device and extended storage media supported by the computer device. The computer-readable storage medium provides storage space that stores the terminal's operating system. Furthermore, this storage space also stores one or more instructions suitable for loading and execution by a processor. These instructions can be one or more computer programs (including program code). It should be noted that the computer-readable storage medium here can be a high-speed RAM memory or a non-volatile memory, such as at least one disk storage device. The processor can load and execute one or more instructions stored in the computer-readable storage medium to implement the steps of the method for determining the prestress of the anti-vibration hammer steel strand in the above embodiments.

[0213] Those skilled in the art will understand that embodiments of the present invention can be provided as methods, systems, or computer program products. Therefore, the present invention can take the form of a completely hardware embodiment, a completely software embodiment, or an embodiment combining software and hardware aspects. Furthermore, the present invention can take the form of a computer program product embodied on one or more computer-usable storage media (including, but not limited to, disk storage, CD-ROM, optical storage, etc.) containing computer-usable program code.

[0214] This invention is described with reference to flowchart illustrations and / or block diagrams of methods, apparatus (systems), and computer program products according to embodiments of the invention. It will be understood that each block of the flowchart illustrations and / or block diagrams, and combinations of blocks in the flowchart illustrations and / or block diagrams, can be implemented by computer program instructions. These computer program instructions can be provided to a processor of a general-purpose computer, special-purpose computer, embedded processor, or other programmable data processing apparatus to produce a machine, such that the instructions, which execute via the processor of the computer or other programmable data processing apparatus, generate instructions for implementing the flowchart illustrations and / or block diagrams. Figure 1 One or more processes and / or boxes Figure 1 A device that provides the functions specified in one or more boxes.

[0215] These computer program instructions may also be stored in a computer-readable storage medium that can direct a computer or other programmable data processing device to function in a particular manner, such that the instructions stored in the computer-readable storage medium produce an article of manufacture including instruction means, which are implemented in a process Figure 1 One or more processes and / or boxes Figure 1 The function specified in one or more boxes.

[0216] These computer program instructions may also be loaded onto a computer or other programmable data processing equipment to cause a series of operational steps to be performed on the computer or other programmable equipment to produce a computer-implemented process, thereby providing instructions that execute on the computer or other programmable equipment for implementing the process. Figure 1 One or more processes and / or boxes Figure 1 The steps of the function specified in one or more boxes.

[0217] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention and not to limit its scope of protection. Although the present invention has been described in detail with reference to the above embodiments, those skilled in the art should understand that after reading the present invention, they can still make various changes, modifications or equivalent substitutions to the specific implementation methods of the application, but these changes, modifications or equivalent substitutions are all within the scope of protection of the claims pending approval.

Claims

1. A pre-stressed damper, characterized by, The utility model relates to a kind of gap type steel strand (1), assembly integral hammer head (3) and anchoring clamp;The gap type steel strand (1) includes center layer round wire (13), intermediate layer profiled wire (12) and outer layer round wire (11) in order from inside to outside;Gap (14) is arranged between the center layer round wire (13) and intermediate layer profiled wire (12), and gap (14) is filled with lubricating grease;And the length of intermediate layer profiled wire (12) and outer layer round wire (11) is shorter than center layer round wire (13);The intermediate layer profiled wire (12) is arch structure; The center layer round wire (13) is connected with one assembly integral hammer head (3) at both ends respectively, and the hollow portion is in the middle position of the end of each assembly integral hammer head (3) away from the center layer round wire (13), and the anchoring clamp is assembled in the hollow portion; The anchoring clamp is used for clamping the center layer round wire (13) after being pre-stressed by external tensioning tool, and the gap type steel strand (1) and assembly integral hammer head (3) are coupled and connected by the center layer round wire (13) after being pre-stressed. The end of the assembly integral hammer head (3) close to the center layer round wire (13) is provided with a center hole; The both ends of the center layer round wire (13) pass through the center hole of the assembly integral hammer head (3) at the end respectively, and the anchoring clamp is clamped on the center layer round wire (13) after being pre-stressed and passing through the center hole; 2. A pre-stressed damper as claimed in claim 1, wherein, The center layer round wire (13) passing through the center hole and clamped by the anchoring clamp is coupled and connected with the assembly integral hammer head (3) provided with the anchoring clamp. The anti-vibration hammer further comprises a wire clamp (2), one end of the wire clamp (2) is clamped in the middle of the outer layer round wire (11), and the other end is sleeved on the external conductor;The assembly integral hammer head (3) is symmetrically distributed on both sides of the wire clamp (2). The assembly integral hammer head (3) comprises a concave hammer head (23) and a convex hammer head (31), the end of the concave hammer head (23) away from the wire clamp (2) is recessed inward and tightly contacts the structure of the convex hammer head (31) protruding outward, the end of the convex hammer head (31) away from the concave hammer head (23) is open and hollow, the opening direction is away from the concave hammer head (23), and the anchoring clamp is assembled in the hollow portion of the convex hammer head (31); 3. A pre-stressed damper as claimed in claim 2, wherein, The center hole comprises a first center hole (22) provided in the concave hammer head and a second center hole (33) provided in the convex hammer head (31), and the center layer round wire (13) passes through the first center hole (22) and the second center hole (33) in order.

4. A pre-stressed damper as claimed in claim 3, wherein, The diameters of the first center hole (22) and the second center hole (33) are smaller than the diameter of the gap type steel strand (1) and larger than the diameter of the center layer round wire (13). The end of the concave hammer head (23) close to the wire clamp (2) is in U-shaped structure, the opening of the U-shaped structure faces the wire clamp, the steel sleeve (21) is fixedly installed in the recessed portion of the opening of the U-shaped structure, and the steel sleeve (21) is sleeved on the outside of the outer layer round wire (11).

5. A pre-stressed damper as claimed in claim 4, wherein, ​ 6. A pre-stressed damper as claimed in claim 4, wherein, ​ 7. A pre-stressed damper as claimed in claim 4, wherein, The upper and lower edges of the hollow part of the convex hammer head (31) are respectively provided with an anchor clamp embedded slot (32) close to the second center hole (33), and the anchor clamp is assembled in the anchor clamp embedded slot (32).

8. A pre-stressed damper as claimed in claim 7, wherein, The anchor clamp comprises an upper clamp piece (41) and a lower clamp piece (42), both of which are wedge-shaped structures, the upper clamp piece (41) is clamped with the anchor clamp embedded slot (32) provided on the upper edge, the lower clamp piece (42) is clamped with the anchor clamp embedded slot (32) provided on the lower edge, and the wedge-shaped structures of the upper clamp piece (41) and the lower clamp piece (42) are opposite after clamping.

9. A pre-stressed damper as claimed in claim 1, wherein, The intermediate layer type line (12) comprises: A plurality of type lines, the cross section of the type line is a quadrilateral with the upper wide and the lower narrow, and the plurality of type lines are extruded to form an arch structure around the center layer circular line (13).

10. A method of determining the pre-stress of a steel strand of a vibration isolator, characterized in that Comprise: The dynamic test is conducted on the non-pre-stressed anti-vibration hammer steel strand to obtain the first dynamic bending stiffness of the anti-vibration hammer steel strand under the impact load; The dynamic test is conducted on the pre-stressed anti-vibration hammer steel strand to obtain the second dynamic bending stiffness of the anti-vibration hammer steel strand under the impact load; Based on the ratio of the first dynamic bending stiffness and the second dynamic bending stiffness of the anti-vibration hammer steel strand under the impact load, the value of the pre-stress is adjusted to obtain the target stress of the anti-vibration hammer steel strand; The anti-vibration hammer steel strand is the gap type steel strand of the anti-vibration hammer of claim 1.

11. A method of determining the pre-stress of a vibration damper steel strand as claimed in claim 10, c h a r a c t e r i s e d b y The adjustment of the value of the pre-stress to obtain the target stress of the anti-vibration hammer steel strand based on the ratio of the first dynamic bending stiffness and the second dynamic bending stiffness of the anti-vibration hammer steel strand under the impact load comprises: If the ratio of the first dynamic bending stiffness and the second dynamic bending stiffness of the anti-vibration hammer steel strand under the same impact load is in the preset stiffness ratio interval, the value of the pre-stress is taken as the target stress of the anti-vibration hammer steel strand; If the ratio of the first dynamic bending stiffness and the second dynamic bending stiffness of the anti-vibration hammer steel strand under the same impact load is not in the preset stiffness ratio interval, the pre-stress is adjusted, the second dynamic bending stiffness of the pre-stressed anti-vibration hammer steel strand is recalculated, and the ratio of the first dynamic bending stiffness and the second dynamic bending stiffness is in the stiffness ratio interval until the value of the pre-stress at this time is taken as the target stress of the anti-vibration hammer steel strand.

12. A method of determining the pre-stress of a vibration isolator steel strand as defined in claim 10, wherein The dynamic test is conducted on the non-pre-stressed anti-vibration hammer steel strand to obtain the first dynamic bending stiffness of the anti-vibration hammer steel strand under the impact load, comprising: The static bending stiffness of the anti-vibration hammer steel strand is obtained by using the weight of the weight applied to one end of the anti-vibration hammer steel strand and the deflection of the anti-vibration hammer steel strand; The damping ratio of the anti-vibration hammer steel strand is obtained by the decay vibration generated after the impact load is applied to one end of the anti-vibration hammer steel strand connected with the hammer head; The vibration signal of the anti-vibration hammer steel strand after the impact load is applied is processed by a data acquisition analyzer to obtain the natural frequency of the anti-vibration hammer steel strand; The first dynamic bending stiffness of the anti-vibration hammer steel strand under the impact load is obtained by using the static bending stiffness, the damping ratio, the natural frequency and the excitation frequency under the impact load of the anti-vibration hammer steel strand, and combining the dynamic bending stiffness calculation formula of the anti-vibration hammer steel strand.

13. A method of determining the pre-stress of a vibration damper steel strand as claimed in claim 12, c h a r a c t e r i s e d b y The static bending stiffness of the anti-vibration hammer steel strand is obtained by using the weight of the weight applied to one end of the anti-vibration hammer steel strand and the deflection of the anti-vibration hammer steel strand, and comprises the following steps: The weight of the weight and the deflection of the anti-vibration hammer steel strand at the yield critical point of the strain gauge are obtained, and the maximum deflection is recorded; The static bending stiffness of the anti-vibration hammer steel strand is obtained by using the weight of the weight and the maximum deflection combined with the calculation formula of the static bending stiffness.

14. A method of determining the pre-stress of a vibration damper steel strand according to claim 13, characterized in that The calculation formula of the static bending stiffness is: Wherein, k represents the static bending stiffness of the damper wire; F represents the load at the free end of the damper wire, i.e. the weight of the connected weight; l represents the distance from the midpoint of the damper wire to the connection between the damper wire and the hammer head; h max represents the maximum deflection.

15. A method of determining the pre-stress of a vibration damper steel strand as defined in claim 12, characterized in that The damping ratio of the anti-vibration hammer steel strand is obtained by the attenuation vibration generated after the impact load is applied to one end of the hammer head connected to the anti-vibration hammer steel strand, and comprises the following steps: The impact load is applied to one end of the hammer head connected to the anti-vibration hammer steel strand, and the vibration attenuation curve of the anti-vibration hammer steel strand is obtained. The damping ratio of the anti-vibration hammer steel strand is obtained according to the amplitude values of two different vibration periods in the vibration attenuation curve combined with the calculation formula of the damping ratio.

16. A method of determining the pre-stress of a vibration isolator steel strand as defined in claim 15, wherein The calculation formula of the damping ratio is: wherein ζ represents the damping ratio of the damper wire; b represents the interval period value of two vibration periods; a represents the a-th vibration period; u a represents the amplitude value of the a-th vibration period in the vibration decay curve of the damper wire; u a+b represents the amplitude value of the a+b-th vibration period in the vibration decay curve of the damper wire.

17. A method of determining the pre-stress of a vibration isolator steel strand as defined in claim 12, wherein The first dynamic bending stiffness of the anti-vibration hammer steel strand under the impact load is obtained by using the static bending stiffness, the damping ratio, the natural frequency of the anti-vibration hammer steel strand and the excitation frequency when the impact load is applied, combined with the dynamic bending stiffness calculation formula of the anti-vibration hammer steel strand, and comprises the following steps: The damping of the anti-vibration hammer steel strand is calculated by using the mass, the damping ratio and the natural frequency of the anti-vibration hammer steel strand combined with the damping calculation formula. The first dynamic bending stiffness of the anti-vibration hammer steel strand under the impact load is calculated by using the static bending stiffness, the damping and the excitation frequency when the impact load is applied, combined with the dynamic bending stiffness calculation formula.

18. A method of determining the pre-stress of a vibration isolator steel strand as defined in claim 17, wherein The dynamic bending stiffness calculation formula is: wherein k d represents the dynamic bending stiffness of the anti-vibration hammer steel strand, k represents the static bending stiffness of the anti-vibration hammer steel strand; m represents the mass of the anti-vibration hammer steel strand; ω represents the excitation frequency of the anti-vibration hammer steel strand; and c represents the damping of the anti-vibration hammer steel strand.

19. A system for determining the pre-stress of a steel strand of a vibration isolator, characterized in that It comprises: The first dynamic bending stiffness determination module is used for dynamic testing of the anti-vibration hammer steel strand without pre-stress to obtain the first dynamic bending stiffness of the anti-vibration hammer steel strand under the impact load; The second dynamic bending stiffness determination module is used for dynamic testing of the anti-vibration hammer steel strand after pre-stress to obtain the second dynamic bending stiffness of the anti-vibration hammer steel strand under the impact load; The target stress determination module is used for adjusting the value of the pre-stress to obtain the target stress of the anti-vibration hammer steel strand based on the ratio of the first dynamic bending stiffness and the second dynamic bending stiffness of the anti-vibration hammer steel strand under the impact load. The anti-vibration hammer steel strand is the gap type steel strand of the anti-vibration hammer of claim 1.

20. A computer device, comprising: It comprises: One or more processors; Memory for storing one or more programs; When the one or more programs are executed by the one or more processors, the determination method of the pre-stress of the anti-vibration hammer steel strand is realized as claimed in any one of claims 10 to 18.

21. A computer-readable storage medium, characterized in that, The computer program is stored thereon, and when the computer program is executed, the determination method of the pre-stress of the anti-vibration hammer steel strand is realized as claimed in any one of claims 10 to 18.

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