Modular expansion joint with damping shock absorber

Abstract

The invention relates to the field of bridge expansion joints, and particularly discloses a modular expansion joint with a damping shock absorber, which comprises a middle beam, side beams, cross beams, rubber sheets and side seats, the side beams are arranged on the two sides of the middle beam, first rubber clamping grooves are formed in the side beams, and second rubber clamping grooves are formed in the two sides of the middle beam; the rubber sheets are arranged on the two sides of the middle beam, the two ends of the rubber sheets are clamped into the first rubber clamping grooves and the second rubber clamping grooves, the cross beam is arranged at the bottom of the middle beam, the side bases are arranged at the bottoms of the side beams, sliding grooves are formed in the side bases, and the cross beam is horizontally arranged in the sliding grooves in a sliding mode. The energy supply unit can supply energy to the magneto-rheological damper, and the magneto-rheological damper is arranged between the middle beam and the side beam. The invention aims to provide a modular expansion joint containing a damping shock absorber so as to solve the technical problem of how to improve the damping effect of the expansion joint.

Description

Technical Field

[0001] This invention relates to the field of bridge expansion joints, and specifically discloses a modular expansion joint with a damping shock absorber. Background Technology

[0002] Bridge expansion joints are important structural components in bridge engineering, used to regulate the relative displacement between beams caused by temperature changes, vehicle loads, and the shrinkage and creep of bridge building materials. Traditional modular expansion joints mainly use a combination of rubber and steel plates, absorbing beam deformation through the tensile and compressive deformation of rubber strips. However, they suffer from limited shock absorption, rubber aging after long-term use, and inaccurate displacement control.

[0003] In the existing technology, some patents have attempted to introduce magnetorheological dampers into expansion joints, such as the eddy current magnetorheological damper disclosed in CN107101588A, the wire rope magnetorheological damper disclosed in CN219174998U, and the spring plate magnetorheological damper disclosed in CN222206018U. These magnetorheological dampers can reduce the cumulative travel of expansion joints and the impact of vehicles passing through to a certain extent, but they have the following shortcomings: First, a single type of magnetorheological damper is difficult to cope with the multi-directional displacement requirements under complex working conditions; second, there is a lack of intelligent control system, which cannot dynamically adjust the damping parameters according to actual displacement changes; third, maintenance is difficult, as the magnetorheological damper is highly integrated with the expansion joint, resulting in long replacement cycles and high costs; fourth, environmental adaptability is insufficient, as the performance of existing magnetorheological dampers degrades significantly in extreme temperature or corrosive environments. Summary of the Invention

[0004] In view of this, the purpose of the present invention is to provide a modular expansion joint with damping shock absorbers to solve the technical problem of how to improve the damping effect of expansion joints.

[0005] To achieve the above objectives, the present invention provides the following technical solution:

[0006] A modular expansion joint with a damping shock absorber includes a center beam, side beams, a crossbeam, rubber sheets, and side seats. The side beams are arranged on both sides of the center beam, and a first rubber groove is provided on the side beams. A second rubber groove is provided on both sides of the center beam. The rubber sheets are arranged on both sides of the center beam, and their two ends are inserted into the first and second rubber grooves. The crossbeam is arranged at the bottom of the center beam, and the side seats are arranged at the bottom of the side beams. A sliding groove is provided inside the side seats, and the crossbeam is horizontally slidably arranged in the sliding groove. The joint also includes a magnetorheological damper and a power supply unit. The power supply unit can supply power to the magnetorheological damper, and the magnetorheological damper is arranged between the center beam and the side beams.

[0007] Optionally, universal connectors are provided at both ends of the magnetorheological damper, and the universal connectors are connected to the adjacent middle beam / side beam.

[0008] Optionally, the universal connector includes an outer connecting base and an inner connecting base, which are universally connected. A damping spring is provided on the magnetorheological damper, and the two ends of the damping spring are respectively connected to the two inner connecting bases of the two universal connectors.

[0009] Optionally, a spring steel layer is provided on the rubber sheet, and the spring steel layer is disposed at the bottom of the rubber sheet or embedded in the middle of the rubber sheet.

[0010] Optionally, the power supply unit includes a flexural power supply module; the flexural power supply module includes a flexural generator, a flexural rectifier, and a flexural energy storage device, the flexural rectifier being electrically connected to the flexural generator and the flexural energy storage device, and the flexural generator being disposed on the central beam and the rubber sheet.

[0011] Optionally, the power supply unit includes a piezoelectric power supply module, which includes a piezoelectric generator, a piezoelectric rectifier, and a piezoelectric energy storage device. The piezoelectric rectifier is electrically connected to the piezoelectric generator and the piezoelectric energy storage device.

[0012] Optionally, the damping spring includes a first spring, a second spring, a third spring, a first separating strip, and a second separating strip; of the first spring, the second spring, and the third spring, the first spring is closer to the side beam, and the third spring is closer to the center beam; both ends of the first separating strip are connected to the first spring and the second spring, and both ends of the second separating strip are connected to the second spring and the third spring; the piezoelectric generator includes a first generator, a second generator, and a third generator, a plurality of the first generators are disposed on the first spring and are arranged opposite each other, a plurality of the second generators are disposed on the second spring and are arranged opposite each other, and a plurality of the third generators are disposed on the third spring and are arranged opposite each other.

[0013] Optionally, the piezoelectric generator includes a plurality of fourth generators, which are arranged in pairs, with each pair of fourth generators being arranged opposite to each other and each fourth generator being mounted on a vibration damping spring.

[0014] Optionally, it also includes a signal conditioning module, which includes a charge amplifier or integrator circuit for converting the charge flow generated by the piezoelectric generator into a signal with respect to the charge quantity Q. i A proportional voltage signal is used to integrate the output signals of each piezoelectric generator to obtain charge signals Q1, Q2, and Q3 that characterize the cumulative compression displacement of each spring; corresponding to the first, second, and third piezoelectric generators, respectively.

[0015] The logic judgment module is used to process each of the charge quantity signals Q. i With the preset displacement threshold Q i,thThe comparison is performed, and a compression degree coefficient α is calculated based on the comparison result; the logic of the logic judgment module in calculating the compression degree coefficient α is as follows: 1) Determine the compression state flag S of each spring. i S i =1 indicates Q i ≥Q i,thQi Otherwise S i =0; 2) Calculate α using the following formula:

[0016]

[0017] Where w i The weights are the coefficients, and w3 > w2 > w1 ≥ 1; Q i,max This is a reference value for the amount of charge corresponding to the maximum allowable compressive displacement of the spring;

[0018] The power distribution module is used to control the electrical power P flowing to the magnetorheological damper according to the compression coefficient α. MR ;

[0019] The power allocation module determines P using a segmented control strategy based on the different threshold ranges of the compression coefficient α. MR :

[0020] When 0 ≤ α < α1, P MR =0;

[0021] When α1≤α<α2, ,and ;

[0022] When α2≤α≤α1 ;

[0023] Where α1 and α2 are preset first and second action thresholds, 0 < α1 < α2 < 1; P i(t) η is the real-time power of each piezoelectric generator; K is the distribution efficiency coefficient; p K boost P is the gain coefficient; MR,max This is the rated maximum input power of the magnetorheological damper.

[0024] A modular expansion joint with a damping shock absorber, the control method comprising the following steps:

[0025] S1: Through integration processing, acquire in real time the charge signals Q1, Q2, Q3 reflecting the compression displacement of each spring; S2: Convert each Q... i With the corresponding displacement threshold Q i,th Compare and calculate the overall compression coefficient α;

[0026] S3: Select the corresponding power supply mode according to the preset range of α value, and distribute the electrical energy generated by piezoelectric power generation to the magnetorheological damper according to the mode, so that it generates the corresponding damping force.

[0027] The working principle and beneficial effects of this solution are as follows:

[0028] First, this solution uses a magnetorheological damper instead of a conventional magnetorheological damper. Magnetorheological dampers offer advantages such as fast response speed, wide damping adjustment range, and low energy consumption, making them highly suitable for expansion joint structures requiring rapid response. Simultaneously, this solution also includes a damping spring and a power supply unit. The damping spring, fitted around the outer ring of the magnetorheological damper, serves to dampen vibrations and dissipate energy, and also acts as a mounting carrier for the power supply unit. The power supply unit generates electricity through piezoelectric or flexural power generation to power the magnetorheological damper. Furthermore, during piezoelectric and flexural power generation, the amount of generated charge can be monitored and calculated to determine the compression of the damping spring, thereby deciding whether to activate the magnetorheological damper. Attached Figure Description

[0029] Figure 1 This is a schematic diagram of the structure of an embodiment;

[0030] Figure 2 This is a partial structural diagram of the magnetorheological damper and the power supply unit.

[0031] The following are the markings in the attached diagram: side beam 1, middle beam 2, rubber sheet 3, spring steel layer 4, universal connector 5, magnetorheological damper 6, first spring 7, second spring 8, third spring 9, first generator plate 10, second generator plate 11, third generator plate 12, outer connecting base 13, inner connecting base 14, first separation bar 15, second separation bar 16. Detailed Implementation

[0032] The following detailed description illustrates the specific implementation method:

[0033] Example 1

[0034] A modular expansion joint with damping shock absorbers, combined with Figure 1 and Figure 2As shown, the system includes a central beam 2, side beams 1, a crossbeam, rubber sheets 3, and side supports. Side beams 1 are positioned on both sides of the central beam 2 and have first rubber grooves. Second rubber grooves are positioned on both sides of the central beam 2. Rubber sheets 3 are positioned on both sides of the central beam 2, with both ends inserted into the first and second rubber grooves. Spring steel layers 4 are positioned on the bottom of the rubber sheets 3. The crossbeam is positioned at the bottom of the central beam 2, and the side supports are positioned at the bottom of the side beams 1. A sliding groove is provided inside the side supports, and the crossbeam slides horizontally within the sliding groove. The system also includes a magnetorheological damper 6 and a power supply unit. The power supply unit can supply power to the magnetorheological damper 6, which is positioned between the central beam 2 and the side beams 1.

[0035] The power supply unit includes a piezoelectric power supply module, which includes several piezoelectric generators, a piezoelectric rectifier, and a piezoelectric energy storage device. The piezoelectric rectifier is electrically connected to the piezoelectric generators and the piezoelectric energy storage device.

[0036] Universal connectors 5 are provided at both ends of the magnetorheological damper 6, and the universal connectors 5 are connected to the adjacent middle beam 2 / side beam 1. The universal connector 5 includes an outer connecting base 13 and an inner connecting base 14, which are universally connected. The magnetorheological damper 6 is provided with a damping spring, and the two ends of the damping spring are respectively connected to the two inner connecting bases 14 of the two universal connectors 5.

[0037] The vibration damping springs include a first spring 7, a second spring 8, a third spring 9, a first separation bar 15, and a second separation bar 16. Of the first spring 7, second spring 8, and third spring 9, the first spring 7 is closer to the side beam 1, and the third spring 9 is closer to the middle beam 2. The two ends of the first separation bar 15 are connected to the first spring 7 and the second spring 8, and the two ends of the second separation bar 16 are connected to the second spring 8 and the third spring 9. The piezoelectric generator includes a first generator 10, a second generator 11, and a third generator 12. Two first generators 10 are mounted on the first spring 7 and are positioned opposite each other. Two second generators 11 are mounted on the second spring 8 and are positioned opposite each other. Two third generators 12 are mounted on the third spring 9 and are positioned opposite each other. The stiffness of the first spring 7, the second spring 8, and the third spring 9 decreases sequentially.

[0038] The power supply unit also includes a signal conditioning module, which includes a charge amplifier or an integrator circuit. The signal conditioning module is used to convert the charge flow generated by the piezoelectric generator into a voltage signal proportional to the charge Qi. At the same time, it is used to integrate the output signals of each piezoelectric generator to obtain charge signals Q1, Q2 and Q3 that characterize the cumulative compression displacement of each spring. These correspond to the first generator 10, the second generator 11 and the third generator 12, respectively.

[0039] The power supply unit also includes a logic judgment module, used to process the various charge quantity signals Q. i With the preset displacement threshold Q i,th The comparison is performed, and a compression coefficient α is calculated based on the comparison result. The logic of the logic judgment module to calculate the compression coefficient α is as follows: 1) Determine the compression state flag S of each spring. i S i =1 indicates Q i ≥Q i,thQi Otherwise S i =0; 2) Calculate α using the following formula:

[0040]

[0041] Where w i The weights are the coefficients, and w3 > w2 > w1 ≥ 1; Q i,max This is a reference value for the amount of charge corresponding to the maximum allowable compressive displacement of the spring;

[0042] The power supply unit also includes a power distribution module, used to control the flow of electrical power P to the magnetorheological damper based on the compression coefficient α. MR ;

[0043] The power distribution module determines P using a segmented control strategy based on the different threshold ranges of the compression coefficient α. MR :

[0044] When 0 ≤ α < α1, P MR =0;

[0045] When α1≤α<α2, ,and ;

[0046] When α2≤α≤α1 ;

[0047] Where α1 and α2 are preset first and second action thresholds, 0 < α1 < α2 < 1; P i(t) η is the real-time power of each piezoelectric generator; K is the distribution efficiency coefficient; p K boost P is the gain coefficient; MR,max This is greater than the rated maximum input power of the magnetorheological damper.

[0048] A modular expansion joint with a damping shock absorber, the control method includes the following steps:

[0049] S1: Through integration processing, acquire in real time the charge signals Q1, Q2, Q3 reflecting the compression displacement of each spring; S2: Convert each Q... i With the corresponding displacement threshold Q i,thCompare and calculate the overall compression coefficient α;

[0050] S3: Select the corresponding power supply mode according to the preset range of α value, and distribute the electrical energy generated by piezoelectric power generation to the magnetorheological damper according to the mode, so that it generates the corresponding damping force.

[0051] Experimental Example 1

[0052] The magnetorheological damper selected is a commercial magnetorheological damper with a rated voltage of 12V, a coil resistance of 8Ω, and a maximum input power of 18W.

[0053] The piezoelectric ceramic sheets serve as piezoelectric generators, with the first, second, and third generators connected in parallel to the control circuit. The control circuit is connected to each piezoelectric generator and the magnetorheological damper via cables. The control circuit includes a signal conditioning module, a logic decision module, and a power distribution module. The signal conditioning module uses an operational amplifier-based charge amplifier circuit to convert the charge generated by the piezoelectric sheets into a voltage signal and integrate it. The logic decision module uses a microcontroller with AD conversion capabilities (such as the STM32F103 series), and the power distribution module uses a PWM-controlled buck-boost converter circuit (such as a circuit based on the LM5176) to regulate the voltage and current supplied to the magnetorheological damper.

[0054] The piezoelectric energy storage device is an electrolytic capacitor with a capacity of 10000μF, connected in parallel to the input terminal of the power distribution module, used to store the surplus electrical energy generated by piezoelectric power generation.

[0055] 1. Method for determining control parameters

[0056] This experimental example details the method for determining each parameter in the claims:

[0057] 1.1 Determination of Structural Parameters

[0058] 1.1.1 First step: Determine the working stroke of the spring

[0059] According to the "General Technical Conditions for Expansion Joints of Highway Bridges" (JT / T 327-2016), for modular expansion joints with a design expansion range of 80mm, the following is determined:

[0060] The design working stroke of the first spring 41 is d1=30mm (corresponding to the normal temperature deformation range of the expansion joint).

[0061] The working stroke of the second spring 42 is designed to be d2=25mm (corresponding to a medium impact deformation range).

[0062] The design working stroke of the third spring 43 is d3=15mm (corresponding to the limit safe deformation range);

[0063] 1.1.2 Second step: Calibrate the charge-displacement relationship

[0064] On the test bench, each spring-piezoelectric assembly underwent a uniform compression test at a speed of 0.5 mm / s, and the relationship between displacement x and accumulated charge Q was recorded. The results of the experiment are as follows:

[0065] First spring 41: Q1(x) = 0.15x (μC / mm), linear correlation coefficient R² = 0.998;

[0066] Second spring 42: Q2(x) = 0.20x (μC / mm), linear correlation coefficient R² = 0.997;

[0067] Third spring 43: Q3(x) = 0.25x (μC / mm), linear correlation coefficient R² = 0.996;

[0068] 1.1.3 Third step: Determine the charge threshold

[0069] Let the compression displacement at which the first spring begins to function effectively be 5mm, then Q 1,th =0.15×5=0.75μC

[0070] Let the compression displacement at which the second spring begins to function effectively be 10mm (the first spring has already been compressed by 5mm), then Q 2,th =0.20×10=2.0μC;

[0071] Let the compression displacement at which the third spring begins to function effectively be 20mm (the first and second springs compress a total of 15mm), then Q 3,th =0.25×20=5.0μC;

[0072] 1.1.4 Step 4: Determine the maximum charge amount

[0073] The maximum compression displacement of the first spring is 30mm, Q 1,max =0.15×30=4.5μC;

[0074] The second spring has a maximum compression displacement of 25mm, Q 2,max =0.20×25=5.0μC;

[0075] The third spring has a maximum compression displacement of 15mm, Q 3,max =0.25×15=3.75μC;

[0076] 1.1.5 Step 5: Determine the weighting coefficients. Based on the spring stiffness ratio k1:k2:k3=5:12:25≈1:2.4:5, take: w1=1.0, w2=2.5, w3=5.0;

[0077] 1.2 Determination of Control Strategy Parameters

[0078] 1.2.1 The first step is to determine the compression thresholds α1 and α2.

[0079] Calculate α1: When the compression reaches the point where the second spring begins to work effectively and the compression amount is 30% of the design value:

[0080] At this point, the first spring is compressed by 15mm (reaching 50% of the design value), Q1=2.25μC, and the excess value=2.25-0.75=1.5μC;

[0081] The second spring is compressed by 5mm (reaching 20% ​​of the design value), Q2=1.0μC, and the excess value=0 (not reaching the threshold).

[0082] The third spring is not compressed;

[0083] α = [1.0 × 1.5 / (4.5 - 0.75) + 2.5 × 0 + 5.0 × 0] / 3 = 0.133; Considering the safety margin, we take α1 = 0.25.

[0084] Calculate α2: When the compression reaches the point where the third spring begins to work effectively and the compression is 20% of the design value:

[0085] The first spring is compressed by 25mm (reaching 83% of the design value), Q1=3.75μC, and the excess value=3.0μC;

[0086] The second spring is compressed by 20mm (reaching 80% of the design value), Q2=4.0μC, and the excess value=2.0μC;

[0087] The third spring is compressed by 3mm (reaching 20% ​​of the design value), Q3=0.75μC, and the excess value=0 (not reaching the threshold).

[0088] α = [1.0 × 3.0 / 3.75 + 2.5 × 2.0 / 3.0 + 5.0 × 0] / 3 = 0.688; Considering the safety margin, we take α2 = 0.70.

[0089] 1.2.2 Second step: Determine the efficiency coefficient η and build a test circuit to measure under 10Hz sinusoidal excitation:

[0090] Total output power P of the piezoelectric element gen =85mW;

[0091] Actual input magnetorheological damper power P MR =48mW;

[0092] The calculated value is η = 48 / 85 = 0.565; considering temperature changes and aging, the design value is η = 0.55.

[0093] 1.2.3 Third step: Determine the gain coefficient K pand K boost

[0094] The gain coefficient must be determined based on the system's energy supply capacity. The instantaneous high-power output of this system mainly relies on the discharge of the energy storage capacitor C (10000μF), which can provide an instantaneous power P. cap,peak The calculated power is approximately 8W. The average power output P of the piezoelectric element is... gen,av It has a power of approximately 35mW and is mainly used to charge capacitors to withstand continuous shocks.

[0095] Determine the proportional gain Kp: set in the medium compression stage (α1≤α<α2), damper power P MR The power increases linearly from 0 to the upper limit of the safe power that the system can sustainably provide (taking P). cap,peak 50%, or 4W). Therefore, the calculation is as follows:

[0096]

[0097] Rounded down, Kp = 8 W.

[0098] Determine the enhancement coefficient K boost : During the severe compression phase (α≥α2), the system should provide stronger damping force, with the target power set at P. cap,peak 80% (i.e., 6.4W). When α = α² = 0.70, the proportional contribution is P. base =Kp×(0.70−0.25)=3.6 W. Therefore, the required additional power is:

[0099]

[0100] To allow for a margin, let K be taken. boost =3 W.

[0101] 1.2.4 Step 4: Verify power constraints

[0102] It is necessary to ensure that, under any circumstances, the calculated P MR The command value shall not exceed the rated power P of the damper. MR,max =18W, and not exceeding the actual power P that the system can provide. sys,max ≈8W.

[0103] In the theoretically worst-case scenario (α=1):

[0104]

[0105] The actual output of the system is limited by the power supply capacity:

[0106]

[0107] Ultimately, 8 W < 18 W, satisfying all safety and physical constraints.

[0108] 2. Implementation of Control Processes

[0109] The control process of this invention includes the following steps:

[0110] Step S101: System Initialization

[0111] After power-on, the microcontroller initializes the AD converter, timer, and PWM module. It clears the charge registers Q1, Q2, and Q3 and loads the preset parameters: Q... i,th Q i,max w i α1, α2, η, K p K boost P MR,max .

[0112] Step S102: Signal Acquisition and Processing

[0113] The output voltage V of each charge amplifier is sampled every 10ms. i(t)

[0114] Calculate the charge increment: ΔQ i =V i(t) ×C fb / k gain C fb For the feedback capacitor (1nF), k gain Gain (100mV / μC)

[0115] Update accumulated charge: Q i =Q i +ΔQ i

[0116] Calculate the current total power generation: P gen(t) =Σ[V i(t) ×I i(t) ], where I i(t) Measured by sampling resistance;

[0117] Step S103: Compression status determination

[0118] For each i (1,2,3):

[0119] If Q i ≥Q i,th Then S i =1, otherwise S i =0;

[0120] Calculate the excess ratio Ri=max(0, Q) i -Q i,th ) / (Qi,max -Q i,th );

[0121] Calculate the compression factor: α = (w1·S1·R1 + w2·S2·R2 + w3·S3·R3) / 3;

[0122] Step S104: Power allocation decision: Select control mode based on α value.

[0123] If α < 0.25, enter energy-saving mode: PMR = 0W, turn off PWM output;

[0124] If 0.25 ≤ α < 0.70, enter proportional control mode:

[0125] Calculate the base power: P base =K p ×(α-0.25)

[0126] Calculate available power: P available =η×P gen(t) +P cap(t) , where P cap(t) Capacitors can provide power

[0127] P MR =min(P base ,P available ,10.8W);

[0128] If α ≥ 0.70, enter enhanced control mode:

[0129] P base =10.8W+K boost ×(α-0.70)

[0130] P available =η×P gen(t) +P cap(t)

[0131] P MR =min(P base ,P available ,18W);

[0132] Step S105: PWM Output and Energy Management

[0133] According to P MR Calculate the target voltage using the magnetorheological damper resistor (8Ω): V target =sqrt(P MR ×8);

[0134] The PWM duty cycle is adjusted using a PID algorithm to make the output voltage track V. target；

[0135] Monitor the voltage V of the energy storage capacitor cap :

[0136] If V cap >15V and P MR < Pavailable Excess energy is stored in the capacitor;

[0137] If V cap <8V and requires additional power, so energy is released from the capacitor;

[0138] Step S106: Safety Monitoring and Fault Handling

[0139] Monitor the magnetorheological damper current; if it exceeds 2A (corresponding to P...) MR If the output exceeds 32W, immediately shut down the output and trigger an alarm.

[0140] Monitor the compression state of each spring; if α > 0.95, issue a warning signal.

[0141] The operation data is uploaded to the monitoring center via wireless module every 24 hours.

[0142] Step S107: Return to the loop and wait for the next 10ms timer interrupt, then return to step S102.

[0143] 3. Performance verification test

[0144] To verify the effectiveness of the device of the present invention, a 1:2 scale test platform was built in the laboratory for comparative testing.

[0145] 3.1.1 Test Platform Setup

[0146] Loading system: MTS hydraulic servo actuators are used to simulate the relative motion of the beam, with a maximum stroke of ±100mm and a maximum loading frequency of 10Hz;

[0147] Test specimen:

[0148] ①Specimen A: Modular expansion joint specimen with the damping device of the present invention installed;

[0149] ②Specimen B: Modular expansion joint specimen with ordinary rubber bearing installed (traditional scheme);

[0150] ③Specimen C: Modular expansion joint specimen without any damping device (blank control);

[0151] Measurement system:

[0152] ① A laser displacement sensor measures the relative displacement between the middle beam and the side beam;

[0153] ② Force sensor measures damping force;

[0154] ③ The data acquisition system has a sampling frequency of 1000Hz;

[0155] 3.1.2 Test Condition Design

[0156] Simulates three typical stress conditions of bridge expansion joints:

[0157] Operating Condition 1: Temperature Cycle (Simulating Day-Night Temperature Difference)

[0158] Displacement curve: triangular wave, amplitude ±20mm, frequency 0.001Hz (period 16.7 minutes).

[0159] Duration: 3 complete cycles;

[0160] Operating Condition 2: Vehicle Braking (Simulating Moderate Impact)

[0161] Displacement curve: half-sine wave, amplitude 15mm, duration 0.5s

[0162] Interval time: 30s

[0163] Number of cycles: 50;

[0164] Condition 3: Earthquake / Strong Wind (Simulating Extreme Impact)

[0165] Displacement curve: sinusoidal sweep, amplitude 25mm, frequency sweep from 1Hz to 5Hz.

[0166] Duration: 30 seconds;

[0167] 3.1.3 Analysis of Experimental Results

[0168] ① Results of temperature cycling condition (condition 1) Table 1 Performance comparison of temperature cycling condition

[0169]

[0170] Analysis: The device of this invention has moderate damping force under temperature cycling, avoiding the problem of excessive damping affecting free expansion and contraction in traditional solutions, and is completely self-powered.

[0171] ② Results of vehicle braking conditions (condition 2) Table 2 Comparison of vehicle braking performance under different conditions

[0172]

[0173] The change in the compressibility coefficient α of specimen A during 50 impact tests. It can be seen that:

[0174] During the first 10 impacts, α was below 0.25, indicating that the system was in energy-saving mode.

[0175] During the 11th to 30th impacts, α was between 0.25 and 0.70, and the system entered proportional control mode.

[0176] After the 31st iteration, α exceeded 0.70, and the system entered enhanced control mode, effectively limiting displacement growth.

[0177] ③ Results of extreme impact conditions (condition 3) Table 3 Performance comparison under extreme impact conditions

[0178]

[0179] ④ Durability test results: After subjecting specimen A to 2 million fatigue tests at a frequency of 2Hz and an amplitude of 10mm:

[0180] Spring stiffness attenuation: First spring 4.2%, Second spring 3.8%, Third spring 5.1%.

[0181] Piezoelectric power generation efficiency degradation: 8.7%

[0182] The control circuit functions normally, and after the parameters are adaptively adjusted, the performance recovers to 95% of the initial value.

[0183] 3.1.4 Experimental Conclusions

[0184] Effectiveness verification: The device of the present invention performs excellently under three working conditions. Compared with the traditional solution, it reduces temperature deformation resistance by 44%, reduces peak impact displacement by 11%-29%, avoids collisions under extreme working conditions, and improves safety margin by 92%.

[0185] Self-powered verification: The device required no external power supply throughout the entire test. Under vehicle braking conditions, the average regenerative power reached 35mW, fully meeting the energy consumption requirements of the control circuit (average power consumption 12mW) and the magnetorheological damper (peak demand 5W, but short duration).

[0186] Intelligent verification: The compression coefficient α can accurately reflect the severity of the relative displacement of the beam. The three-stage control strategy realizes a smooth transition from "no intervention" to "proportional intervention" and then to "strong intervention".

[0187] 4. Parameter Adjustment Range Description

[0188] Those skilled in the art can adjust the parameters according to different bridge requirements; the recommended range is as follows:

[0189] Spring stiffness ratio k1:k2:k3:1:(1.5-3):(3-8);

[0190] Weighting coefficients w1:w2:w3:1:(1.2-3):(2-6);

[0191] Threshold α1: 0.15-0.35, preferably 0.20-0.30;

[0192] Threshold α2: 0.60-0.85, preferably 0.65-0.75;

[0193] Efficiency coefficient η: 0.4-0.7, preferably 0.5-0.6;

[0194] Proportional Gain K p The value is determined based on the power capacity of the magnetorheological damper, and is generally (0.5-2)×P. MR,max ;

[0195] Enhancement coefficient K boost :(0.1-0.5)×P MR,max

[0196] The specific optimization of the above parameters can be carried out using optimization methods such as response surface methodology and genetic algorithms, with the objective functions of minimizing beam end displacement, maximizing energy recovery, and minimizing impact force for multi-objective optimization.

[0197] Example 2

[0198] The difference from Embodiment 1 lies in the use of a flexural power supply module. This module includes a flexural generator, a flexural rectifier, and a flexural energy storage device. The flexural rectifier is electrically connected to the flexural generator and the energy storage device. The flexural generator is mounted on the central beam and the rubber sheet. This solution employs flexural power generation, a novel energy conversion method. Chinese Patent Application No. 202511361777.5 discloses related applications of flexural power generation.

[0199] Example 3

[0200] The difference from Embodiment 1 is that the damping spring is only provided in one section, and the piezoelectric generator includes several fourth generators. The several fourth generators are arranged in pairs, and each group of fourth generators is arranged opposite to each other and the fourth generators are all arranged on the damping spring.

[0201] In Examples 2 and 3, the method of determining the compression of the spring by charge monitoring has not yet been studied. Instead, a displacement sensor can be directly set up for monitoring, and the start and stop of the magnetorheological damper can be controlled based on the results of the displacement sensor.

[0202] The above descriptions are merely embodiments of the present invention, and common knowledge regarding specific structures and characteristics in the solutions is not described in detail here. It should be noted that those skilled in the art can make various modifications and improvements without departing from the structure of the present invention, and these should also be considered within the scope of protection of the present invention. These modifications and improvements will not affect the effectiveness of the implementation of the present invention or its practicality.

Claims

1. A damping damper containing analog expansion joint, comprising a middle beam, a side beam, a cross beam, a rubber sheet and a side seat, the side beam is arranged on both sides of the middle beam, the first rubber clamping groove is arranged on the side beam, the second rubber clamping groove is arranged on both sides of the middle beam, the rubber sheet is arranged on both sides of the middle beam and the both ends are clamped into the first rubber clamping groove and the second rubber clamping groove, the cross beam is arranged at the bottom of the middle beam, the side seat is arranged at the bottom of the side beam, the sliding groove is arranged inside the side seat, and the cross beam is horizontally arranged in the sliding groove, characterized in that: The magnetorheological damper and the energy supply unit are further included, and the energy supply unit is capable of supplying energy to the magnetorheological damper arranged between the middle beam and the side beam.

2. The modular expansion joint containing a damper according to claim 1, wherein: Universal connectors are arranged at two ends of the magnetorheological damper, and the universal connectors are connected with adjacent middle beams / side beams.

3. A modular expansion joint containing a damper according to claim 2, wherein: The universal connector includes an outer connecting base and an inner connecting base, and the outer connecting base and the inner connecting base are connected in a universal manner.

4. The modular expansion joint containing a damper according to claim 3, wherein: A spring steel layer is arranged on the rubber sheet, and the spring steel layer is arranged at the bottom of the rubber sheet or embedded in the middle part of the rubber sheet.

5. The modular expansion joint containing a damper according to claim 4, wherein: The energy supply unit includes a flexoelectric energy supply module, and the flexoelectric energy supply module includes a flexoelectric power generation sheet, a flexoelectric rectifier, and a flexoelectric energy storage device.

6. The modular expansion joint containing a damper according to claim 4, wherein: The energy supply unit includes a piezoelectric energy supply module, and the piezoelectric energy supply module includes a piezoelectric power generation sheet, a piezoelectric rectifier, and a piezoelectric energy storage device.

7. A modular expansion joint containing a damper according to claim 6, wherein: The damping spring includes a first spring, a second spring, a third spring, a first separation strip, and a second separation strip. The first separation strip is connected with the first spring and the second spring at two ends, and the second separation strip is connected with the second spring and the third spring at two ends.

8. The modular expansion joint with a damper according to claim 6, characterized in that: The piezoelectric power generation sheet includes a first power generation sheet, a second power generation sheet, and a third power generation sheet.

9. The modular expansion joint of claim 7, wherein: The piezoelectric power generation sheet includes a plurality of fourth power generation sheets, and each group of the fourth power generation sheets is arranged oppositely and arranged on the damping spring. The signal conditioning module includes a charge amplifier or an integration circuit for converting the charge current generated by the piezoelectric power generation sheet into a voltage signal proportional to the charge quantity Q i The output signal of each piezoelectric power generation sheet is integrated to obtain the charge quantity signals Q1, Q2 and Q3 representing the cumulative compression displacement of each spring, corresponding to the first piezoelectric power generation sheet, the second piezoelectric power generation sheet and the third piezoelectric power generation sheet respectively. A logic judging module is configured to compare each of the charge quantity signals Q i with a preset displacement threshold Q i,th , and calculate a compression degree coefficient a based on a comparison result; the logic of the logic judging module for calculating the compression degree coefficient a is: 1) determining a compression state flag S i of each spring, wherein S i =1 represents Q i ≥Q i,thQi , otherwise S i =0; 2) calculating a according to the following formula: where w i is a weight coefficient, and w3> w2> w1≥ 1; Q i,max is a reference value of the amount of electric charge corresponding to the maximum compression displacement allowed by the corresponding spring; a power distribution module, configured to control electric power P flowing to the MR damper according to the compression degree coefficient α MR ; The power distribution module adopts a segmented control strategy to determine P according to different threshold intervals of the compression degree coefficient α MR : P = 0 when 0 < a < ai MR = 0; when a1 < a < a2, and ; when a2< a < ai, ; Wherein, α1, α2 are preset first and second action threshold values, 0 < α1 < α2 < 1; P i(t) P is the real-time power of each piezoelectric power generation sheet; η is a distribution efficiency coefficient; K p , K boost is a gain coefficient; P MR,max is the rated maximum input power of the magneto-rheological damper.

10. The modular expansion joint containing a damper according to claim 9, wherein, The control method includes the following steps: S1: through integral processing, real-time acquisition of charge quantity signals Q1, Q2, Q3 reflecting the compression displacement of each spring; S2: comparing each Q i with the corresponding displacement threshold value Q i,th comparison, calculation of the overall compression degree coefficient α; S3: According to the preset interval where the alpha value is located, the corresponding energy supply mode is selected, and the electric energy generated by the piezoelectric power generation is distributed to the magnetorheological damper according to the mode, so that the corresponding damping force is generated.

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