Test bench for automobile rolling collision test

Abstract

The invention relates to the technical field of collision tests, in particular to a test bed for an automobile rolling collision test, which comprises a base, a sliding table and a rack, the sliding table is in sliding fit with the base, the rack is arranged on the base, the rack comprises a left stand column and a right stand column which are symmetrically arranged, and rotating arms are respectively positioned on two sides of the sliding table and arranged between the left stand column and the right stand column; the left stand column and the right stand column are in sliding fit with sliding block bases respectively, the two ends of the rotating arm are supported on the sliding block bases, rotating motors are arranged on the sliding block bases and are in transmission connection with the rotating arm, the upper ends of the left stand column and the right stand column are connected through a motor installation frame, and a lifting motor is arranged on the motor installation frame and is in transmission connection with a transmission shaft. The transmission shaft is connected with the sliding block base of the left stand column through a first chain transmission mechanism, and the transmission shaft is connected with the sliding block base of the right stand column through a second chain transmission mechanism. The problems of poor repeatability and poor test result reliability caused by difficulty in controlling the vertical speed of the existing rolling collision test are solved.

Description

Technical Field

[0001] This invention relates to the field of collision testing technology, and more specifically to a test bench for automobile rollover collision testing. Background Technology

[0002] Currently, the main testing methods for simulating car rollover accidents include roof crush tests, trolley roller rollover tests, and repeatable rollover tests. Roof crush tests are primarily used to measure the crush resistance of a car roof under quasi-static conditions. While this method provides important information about the roof structure's strength, it cannot realistically reproduce the dynamic collision process between the roof and the ground in a rollover accident. Therefore, it cannot comprehensively assess a vehicle's safety in actual rollover accidents. Trolley roller rollover tests attempt to compensate for these shortcomings by simulating the rollover process under specific conditions, but the simulated vehicle motion patterns still differ significantly from real-world rollover accidents, representing only a very limited range of rollover scenarios. Furthermore, because the vehicle's trajectory is uncontrollable during the test, this method has poor repeatability, limiting its application value in scientific research and technological verification. Repeatable rollover tests, such as CRIS (Controlled Rollover System) and JRS (Jordan Rollover Impact System), simulate the vehicle rotation process in a rollover accident through a spin mechanism. During the rollover, the test vehicle simultaneously impacts the test platform at a certain vertical speed, thus simulating a rollover accident. Currently, rollover tests typically involve setting the test vehicle at a certain height before the test and then allowing it to fall freely to meet the required vertical velocity. This method of applying vertical velocity is unpredictable, detrimental to the repeatability of rollover tests, and difficult to control, making it unsuitable for all operating conditions and limiting its application in safety assessments, thus affecting the reliability of rollover test results. Therefore, existing rollover test benches still have significant shortcomings in vertical velocity control and test repeatability, urgently requiring further optimization and improvement. Summary of the Invention

[0003] The present invention aims to provide a test bench for automobile rollover collision testing, so as to solve the problems of poor repeatability and poor reliability of test results caused by the difficulty in controlling the vertical velocity in existing rollover collision tests.

[0004] To achieve the above objectives, the present invention adopts the following technical solution: a test bench for automobile rollover collision testing, comprising a base, a slide table, and a frame. The slide table is slidably fitted on the base, and the frame is provided on the base. The frame includes a left column and a right column symmetrically arranged, located on both sides of the slide table. A rotating arm is provided between the left column and the right column. Sliding blocks are slidably fitted on the left column and the right column. The two ends of the rotating arm are supported on the sliding blocks. A rotary motor is provided on the sliding blocks. The rotary motor is drivenly connected to the rotating arm. The upper ends of the left column and the right column are connected by a motor mounting bracket. A lifting motor is provided on the motor mounting bracket. The lifting motor is drivenly connected to a drive shaft. The drive shaft is connected to the sliding block of the left column through a first chain drive mechanism, and the drive shaft is connected to the sliding block of the right column through a second chain drive mechanism.

[0005] The working principle and beneficial effects of this solution: The base, slide, and frame adopt a modular design for easy installation, disassembly, and maintenance. Symmetrical left and right columns ensure the stability and balance of the test bench. The slide can slide on the base, simulating the lateral movement of a vehicle during rollover, improving the realism of the test. The slider seat can slide on the columns, facilitating adjustment of the rotating arm height to adapt to different vehicle models and test requirements. The sliding fit design reduces complex mechanical structures and lowers the failure rate. By installing a rotary motor on the slider seat to drive the rotating arm, precise angle adjustment and rollover control of the vehicle can be achieved. The chain drive mechanism transmits power from the lifting motor to the slider seats on both sides. The lifting motor drives the slider seats to move up and down through the drive shaft and chain drive mechanism, achieving precise adjustment of the rotating arm height. The left and right uprights are connected by the first and second chain drive mechanisms respectively, ensuring synchronous movement on both sides and avoiding tilting or imbalance. The height of the rotating arm can be flexibly adjusted through the lifting motor and chain drive mechanism to meet the rollover test requirements of different vehicle models. The rotating motor and lifting motor are automatically controlled, making operation simple and reducing manual intervention. The chain drive mechanism has a simple structure, is easy to maintain, and has high transmission efficiency.

[0006] Preferably, the system further includes a left guide post and a right guide post located on both sides of the slide table. The upper ends of the left and right guide posts are connected to the motor mounting bracket. A first guide block slides on the left guide post, and a second guide block slides on the right guide post. The first guide block is fixedly connected to the slider seat on the left column, and the second guide block is fixedly connected to the slider seat on the right column. By introducing guide posts and guide blocks, the structural rigidity of the entire system is further enhanced. The guiding system can assist the chain drive mechanism in achieving synchronous lifting and lowering of the left and right slider seats, preventing tilting problems caused by uneven load on one side or mechanical errors, maintaining the horizontal state of the rotating arm, ensuring the correct posture of the vehicle during the rollover process, reducing vibration or displacement caused by external forces, and ensuring the accuracy and reliability of test data. The design of the guide posts and guide blocks makes the up-and-down movement of the slider seats more precise and stable. The enhanced structural stability and motion accuracy not only improve the quality of the test but also increase the safety of operation, effectively preventing accidents. The sliding fit between the guide posts and guide blocks provides a smooth motion path, reducing friction and wear, helping to extend the service life of key components and reduce maintenance costs and frequency.

[0007] Preferably, the lifting motor and the drive shaft are connected via a reduction mechanism. The reduction mechanism converts the high-speed, low-torque output of the lifting motor into a low-speed, high-torque output. This increased torque allows for more effective driving of heavier loads, improves system control accuracy, and ensures smooth and reliable movement of the slider and its related components. The reduction mechanism also provides a smoother power output, reduces speed fluctuations and potential vibrations, and enhances the overall stability of the equipment.

[0008] More preferably, the reduction mechanism includes a third driving wheel, a third driven wheel, and a third transmission chain. The diameter of the third driving wheel is smaller than that of the third driven wheel. The third driving wheel is mounted on the motor shaft of the lifting motor, and the third driven wheel is mounted on the transmission shaft. The third driving wheel and the third driven wheel are connected by the third transmission chain. Chain transmission can withstand high loads while ensuring high efficiency, ensuring effective power transmission, and reducing energy loss. The reduction ratio can be adjusted by changing the diameter ratio of the driving wheel and the driven wheel to meet the speed and torque requirements under different test conditions, providing greater operational flexibility.

[0009] Preferably, the first chain drive mechanism includes a first drive wheel, a first guide wheel, a first driven wheel, a first fixed wheel, a first tension wheel shaft, a first tension wheel, and a first drive chain. The first drive wheel is mounted on the drive shaft, the first guide wheel is mounted on the slider seat of the left column, and the first guide wheel moves along the first drive chain to drive the slider seat on the left column to slide on the left column. The first driven wheel is mounted on the left column below the slider seat, the first fixed wheel is mounted on the motor mounting bracket above the slider seat of the left column, the first tension wheel shaft is supported on the motor mounting bracket and located below the first fixed wheel, the first tension wheel is mounted on the first tension wheel shaft, and the first drive chain is mounted on the first drive wheel, the first guide wheel, the first driven wheel, the first fixed wheel, and the first tension wheel.

[0010] Preferably, the second chain drive mechanism includes a second driving wheel, a second guide wheel, a second driven wheel, a second fixed wheel, a second tension wheel shaft, a second tension wheel, and a second drive chain. The second driving wheel is mounted on the drive shaft, the second guide wheel is mounted on the slider seat of the right column, and the second guide wheel moves along the second drive chain to drive the slider seat on the right column to slide on the right column. The second driven wheel is mounted on the right column below the slider seat, the second fixed wheel is mounted on the motor mounting bracket above the slider seat of the right column, the second tension wheel shaft is supported on the motor mounting bracket and located below the second fixed wheel, the second tension wheel is mounted on the second tension wheel shaft, and the second drive chain is mounted on the second driving wheel, the second guide wheel, the second driven wheel, the second fixed wheel, and the second tension wheel.

[0011] Both the first and second chain drive mechanisms employ a multi-wheel system, ensuring efficient power transmission from the drive shaft to the slider seat. This allows for more precise adjustment of the slider seat position, with the chain guided and supported at multiple points. This reduces operational deviations and helps improve the overall system's response speed and operational efficiency. The fixed wheel and tension wheel not only help maintain appropriate chain tension and reduce slippage or tooth skipping caused by slack, but also effectively distribute the pressure on the chain, thereby extending its service life and improving the system's reliability and stability.

[0012] Preferably, the system further includes a slide drive device, which includes a cylinder and brake pads. A guide rail is provided on the base, and the slide slides on the base via the guide rail. The brake pads are mounted on the guide rail. The guide rail provides precise guidance for the slide, ensuring smooth and linear movement along a predetermined path, reducing swaying or deviation during movement, and improving the stability and reliability of the entire system.

[0013] Preferably, when the slide drive device applies a sine wave to the slide, the expression for the slide launch time is as follows:

[0014]

[0015] In the formula, T1 is the launch time of the slide during a sine wave, and v z Let a be the vertical collision velocity of the test vehicle corresponding to the current test conditions. z σ represents the vertical acceleration of the test vehicle during the current test conditions, and σ is the period correction coefficient.

[0016] Calculating the launch time of the slide based on the test conditions and loading waveform helps ensure the consistency of test conditions for each test, thereby reducing errors caused by improper control of dependent variables and improving the reliability and repeatability of experimental data.

[0017] More preferably, when the slide drive device applies a trapezoidal wave to the slide, the expression for the slide's emission time is as follows:

[0018]

[0019] In the formula, T2 is the launch time of the slide table when the trapezoidal wave is formed, and v z Let a be the vertical collision velocity of the test vehicle corresponding to the current test conditions. z v represents the vertical acceleration of the test vehicle during the current test conditions. x Let a be the collision velocity of the slide table corresponding to the current test conditions. x This represents the collision speed of the slide table under the current test conditions.

[0020] Adjusting the relevant waveforms according to specific test requirements and using the launch time of the slide platform calculated based on specific parameters not only allows the test vehicle to collide with the slide platform with a preset vertical velocity and a corresponding horizontal velocity, thus improving the accuracy and effect of the rollover collision test, but also enhances the safety and flexibility of the entire test process. It can also minimize unnecessary waiting time and improve the efficiency of the entire test process while ensuring the quality of the experiment.

[0021] More preferably, during the test, the height between the slider seat and the slide table surface satisfies the following relationship:

[0022]

[0023] In the formula, h is the height between the slider seat and the slide table surface, and v z The vertical collision velocity of the test vehicle corresponding to the current test condition; a z This represents the vertical acceleration of the test vehicle during the current test conditions.

[0024] By accurately calculating the drop height of the test vehicle, not only can the vertical velocity be accurately controlled, which helps improve the quality of experimental data and provides more accurate basic information for subsequent data analysis, but it can also reduce the number of unnecessary repeated tests, saving time and costs. At the same time, reasonable parameter settings can also help optimize the efficiency of energy and other resource use and achieve optimal resource allocation. Attached Figure Description

[0025] Figure 1 This is an isometric view of the present invention;

[0026] Figure 2 for Figure 1 Enlarged view of point A in the middle;

[0027] Figure 3 This is a top view of the present invention;

[0028] Figure 4 This is a front view of the present invention;

[0029] Figure 5 This is a right view of the present invention;

[0030] Figure 6 for Figure 5 Sectional view along the AA direction.

[0031] The markings in the accompanying drawings include: slide table 1, frame 2, left column 21, right column 22, left guide column 23, right guide column 24, left support column 25, right support column 26, drive shaft 3, rotary motor 4, input shaft 41, slider seat 5, first guide block 51, second guide block 52, connector 6, rotating arm 7, lifting motor 8, third drive wheel 81, third driven wheel 82, third transmission chain 83, first drive wheel 91, first guide wheel 97, first driven wheel 92, first fixed wheel 93, first tension wheel shaft 94, first tension wheel 95, first transmission chain 96, second drive wheel 11, second guide wheel 17, second driven wheel 12, second fixed wheel 13, second tension wheel shaft 14, second tension wheel 15, second transmission chain 16, cylinder 10. Detailed Implementation

[0032] The following detailed description provides further details on specific implementation methods: See [link / reference] Figures 1 to 6A test bench for automobile rollover collision testing includes a base, a slide table 1, and a frame 2. The base is provided with a sliding groove, and a guide rail is provided at the opening of the sliding groove. The slide table 1 slides on the base via the guide rail. The test bench also includes a slide table 1 drive device, which includes a cylinder 10 and a brake pad. The cylinder 10 is located in the sliding groove, and the brake pad is disposed on the guide rail. A frame 2 is provided on the base. The frame 2 includes a left column 21 and a right column 22 symmetrically arranged on both sides of the slide table 1. A rotating arm 7 is provided between the left column 21 and the right column 22. Sliding slider seats 5 are slidably engaged on the left column 21 and the right column 22. The two ends of the rotating arm 7 are supported on the sliding slider seats 5. A rotary motor 4 is provided on the sliding slider seats 5. The rotary motor 4 is connected to the rotating arm 7. A connecting member 6 is provided between the rotating arm 7 and the rotary motor 4. The connecting member 6 has multiple mounting holes, including a first mounting hole and a second mounting hole. The first mounting hole is used to install the rotating arm 7. The shaft of the rotary motor 4 is fixedly connected to one end of an input shaft 41. The other end of the input shaft 41 passes through the slider and is installed in the second mounting hole of the connecting member 6. The first mounting hole and the second mounting hole have the same structure. The cross-section of the input shaft 41 is T-shaped. The head of the T-shape extends into the second mounting hole and is fixed. The tail of the T-shape passes through the sliding slider seat and is fixedly connected to the rotary motor 4. The head of the T-shape has the same structure as the end of the rotating arm. The rotating arm and the rotary motor transmit power through a connector. By mounting the rotating arm and rotary motor in different mounting holes, the rotation center during vehicle testing can be adjusted, making it suitable for different vehicle models and operating conditions. The rotating arm 7 has multiple test vehicle mounting holes for mounting test vehicles. The upper ends of the left column 21 and right column 22 are connected by a motor mounting bracket. The motor mounting bracket is equipped with a lifting motor 8, which is connected to a drive shaft 3. The drive shaft 3 is connected to the slider seat 5 of the left column 21 via a first chain drive mechanism, and to the slider seat 5 of the right column 22 via a second chain drive mechanism.

[0033] It also includes a left guide post 23 and a right guide post 24 located on both sides of the slide table 1. The upper ends of the left guide post 23 and the right guide post 24 are connected to the motor mounting bracket. The left guide post 23 is slidably fitted with a first guide block 51, and the right guide post 24 is slidably fitted with a second guide block 52. The first guide block 51 is fixedly connected to the slider seat 5 on the left column 21, and the second guide block 52 is fixedly connected to the slider seat 5 on the right column 22.

[0034] It also includes a left support column 25 and a right support column 26 located on both sides of the slide table 1, with the upper ends of the left support column 25 and the right support column 26 connected to the motor mounting bracket. Adding support columns significantly improves the rigidity and stability of the entire test bench frame. The support columns help distribute and bear the weight from the slider seat, rotating arm, and the vehicle under test, thereby increasing the load capacity of the entire system. Especially when performing high-impact or high-speed rollover tests, stronger structural support can effectively reduce system vibration and sway, ensuring stable operation of the equipment. By providing additional support points, the support columns help maintain the stability of the slider seat and its related components during movement, improving the motion accuracy throughout the test process, thereby improving the accuracy and reliability of the test results.

[0035] The left column 21 is located between the left guide column 23 and the left support column 25. The left column 21 is connected to the left guide column 23 and the left support column 25 through crossbeams. The right column 22 is located between the right guide column 24 and the right support column 26. The right column 22 is connected to the right guide column 24 and the right support column 26 through crossbeams.

[0036] The lifting motor 8 is connected to the drive shaft 3 via a reduction mechanism. The reduction mechanism includes a third driving wheel 81, a third driven wheel 82, and a third drive chain 83. The diameter of the third driving wheel 81 is smaller than that of the third driven wheel 82. The third driving wheel 81 is mounted on the motor shaft of the lifting motor 8, and the third driven wheel 82 is mounted on the drive shaft 3. The third driving wheel 81 and the third driven wheel 82 are connected by the third drive chain 83.

[0037] The first chain drive mechanism includes a first drive wheel 91, a first guide wheel 97, a first driven wheel 92, a first fixed wheel 93, a first tension wheel 95, a first tension wheel shaft 94, a first tension wheel 95, and a first drive chain 96. The first drive wheel 91 is mounted on the drive shaft 3, and the first guide wheel 97 is mounted on the slider seat 5 of the left column 21. The first guide wheel 97 moves along the first drive chain 96 to drive the slider seat 5 on the left column 21 to slide on the left column 21. The first driven wheel 92 is mounted on the first drive chain 96. The first fixed wheel 93 is mounted on the left column 21 below the slider seat 5. The first tension wheel 95 is mounted on the motor mounting bracket above the slider seat 5 of the left column 21. The first tension wheel 95 and the first tension wheel shaft 94 are supported on the motor mounting bracket and located below the first fixed wheel 93. The first tension wheel 95 is mounted on the first tension wheel shaft 94. The first transmission chain 96 is mounted on the first drive wheel 91, the first guide wheel 97, the first driven wheel 92, the first fixed wheel 93, and the first tension wheel 95. The second chain drive mechanism includes a second driving wheel 11, a second guide wheel 17, a second driven wheel 12, a second fixed wheel 13, a second tension wheel 15, a second tension wheel shaft 14, a second tension wheel 15, and a second drive chain 16. The second driving wheel 11 is mounted on the drive shaft 3, and the second guide wheel 17 is mounted on the slider seat 5 of the right column 22. The second guide wheel 17 moves along the second drive chain 16 to drive the slider seat 5 on the right column 22 to slide on the right column 22. The second driven wheel 12 is mounted on the drive shaft 3. The second fixed wheel 13 is mounted on the right column 22 below the slider seat 5. The second tension wheel 15 is mounted on the motor mounting bracket above the slider seat 5 of the right column 22. The second tension wheel 15 and the second tension wheel shaft 14 are supported on the motor mounting bracket and located below the second fixed wheel 13. The second tension wheel 15 is mounted on the second tension wheel shaft 14. The second transmission chain 16 is mounted on the second drive wheel 11, the second guide wheel 17, the second driven wheel 12, the second fixed wheel 13, and the second tension wheel 15.

[0038] During the experiment, the height between the slider seat and the slide table surface must satisfy the following relationship:

[0039]

[0040] In the formula, h is the height between the slider seat and the slide table surface, and v z The vertical collision velocity of the test vehicle corresponding to the current test condition; a z This represents the vertical acceleration of the test vehicle during the current test conditions.

[0041] The waveform loaded by the slide can be either a sine wave or a trapezoidal wave. This embodiment uses a sine wave, while another embodiment uses a trapezoidal wave.

[0042] Preferably, when the slide drive device applies a sine wave to the slide, the expression for the slide launch time is as follows:

[0043]

[0044] In the formula, T1 is the launch time of the slide during a sine wave, and v z Let a be the vertical collision velocity of the test vehicle corresponding to the current test conditions. z σ represents the vertical acceleration of the test vehicle during the current test conditions, and σ is the period correction coefficient.

[0045] Preferably, when the slide drive device applies a trapezoidal wave to the slide, the expression for the slide's emission time is as follows:

[0046]

[0047] In the formula, T2 is the launch time of the slide table when the trapezoidal wave is formed, and v z Let a be the vertical collision velocity of the test vehicle corresponding to the current test conditions. z v represents the vertical acceleration of the test vehicle during the current test conditions. x Let a be the collision velocity of the slide table corresponding to the current test conditions. x This represents the collision speed of the slide table under the current test conditions.

[0048] Preferably, the torque of the lifting motor during the test has the following relationship:

[0049] T z =μ(a z -g)mR 81

[0050] In the formula, T z R is the lifting motor torque, m is the total mass of the rotating arm, vehicle body, and dummy during the test, and R is the torque of the lifting motor. 81 Let g be the major diameter of the third driving gear, g be the acceleration due to gravity, μ be the friction correction coefficient, and a be the coefficient of friction. z This represents the vertical acceleration of the test vehicle during the current test conditions.

[0051] Before the test, this invention determines the vertical collision velocity v of the test vehicle based on the current working conditions required for the rollover collision test. z The vertical acceleration a of the test vehicle upon collision z Collision speed of the sliding platform v x Collision speed of the sliding platform a x The test vehicle's collision speed is used to determine the test configuration parameters, which include the test vehicle's drop height, rotary motor speed, slide launch time, test vehicle drop time, and slide test waveform. It also includes parameters based on the test vehicle's own parameters (i.e., overall mass m) and the test vehicle's vertical acceleration a during collision. zThe major diameter of the motor gear, i.e., the major diameter R of the third driving gear. 81 Calculate the lifting motor torque T during the test. z .

[0052] In this embodiment, the overall mass m of the rotating arm, vehicle body, and dummy is 1.2t, the friction correction coefficient is 1.05, the major diameter of the motor gear is 0.5m, and the vertical collision velocity v of the test vehicle corresponding to the current test condition is... z The vertical acceleration a of the test vehicle under the current test conditions is 6 m / s². z 12m / s 2 , where is the collision velocity 'a' of the slide table under the current test conditions. x The value is 20g, and the corresponding sliding table collision velocity v under the current test conditions is... x The test speed was 50 km / h, and the test vehicle rotation speed was 200° / s. The test configuration parameters calculated by the above method were as follows: the height between the slider seat and the slide table surface was 1.5 m, the rotation motor speed was 200° / s, the lifting motor torque was 1890 Nm, the launch time of the trapezoidal wave slide table was 445 ms, the launch time of the sine wave was 391 ms, and the test vehicle descent time was 0 ms.

[0053] The above descriptions are merely embodiments of the present invention, and common knowledge such as specific technical solutions and / or characteristics are 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 technical solutions 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 the practicality of the patent. The scope of protection claimed in this application should be determined by the content of its claims, and the specific embodiments described in the specification can be used to interpret the content of the claims.

Claims

1. A test bench for automobile rollover collision test, characterized in that: It includes a base, a slide and a frame, the base is slidably matched with the slide, the base is provided with a frame, the frame includes a left column and a right column symmetrically arranged, which are respectively located on both sides of the slide, a rotating arm is arranged between the left column and the right column, the left column and the right column are respectively slidably matched with a slider seat, both ends of the rotating arm are supported on the slider seat, a rotating motor is provided on the slider seat, the rotating motor is transmission-connected with the rotating arm, the upper ends of the left column and the right column are connected through a motor mounting frame, a lifting motor is provided on the motor mounting frame, the lifting motor is transmission-connected with a transmission shaft, the transmission shaft is connected to the slider seat of the left column through a first chain transmission mechanism, and the transmission shaft is connected to the slider seat of the right column through a second chain transmission mechanism.

2. The test bench for automobile rollover collision test according to claim 1, characterized in that: It also includes a left guide column and a right guide column respectively located on both sides of the slide, the upper ends of the left guide column and the right guide column are connected to the motor mounting frame, the left guide column slides with a first guide block, the right guide column slides with a second guide block, the first guide block is fixedly connected to the slider seat on the left column, and the second guide block is fixedly connected to the slider seat on the right column.

3. The test bench for automobile rollover collision test according to claim 1, characterized in that: The lifting motor is connected to the transmission shaft via a speed reduction mechanism.

4. The test bench for automobile rollover collision test according to claim 3 is characterized in that: The deceleration mechanism includes a third driving wheel, a third driven wheel, and a third transmission chain. The diameter of the third driving wheel is smaller than that of the third driven wheel. The third driving wheel is arranged on the motor shaft of the lifting motor, and the third driven wheel is arranged on the transmission shaft. The third driving wheel and the third driven wheel are connected by a third transmission chain.

5. The test bench for automobile rollover collision test according to claim 1, characterized in that: The first chain transmission mechanism includes a first driving wheel, a first guide wheel, a first driven wheel, a first fixed wheel, a first tensioning wheel shaft, a first tensioning wheel, and a first transmission chain, the first driving wheel is arranged on the transmission shaft, the first guide wheel is installed on the slider seat of the left column, the first guide wheel moves along the first transmission chain to drive the slider seat on the left column to slide on the left column, the first driven wheel is installed on the left column and is located below the slider seat, the first fixed wheel is installed on the motor mounting frame and is above the slider seat of the left column, the first tensioning wheel shaft is supported on the motor mounting frame and is located below the first fixed wheel side, the first tensioning wheel is installed on the first tensioning wheel shaft, and the first transmission chain is installed on the first driving wheel, the first guide wheel, the first driven wheel, the first fixed wheel, and the first tensioning wheel.

6. The test bench for automobile rollover collision test according to claim 1, characterized in that: The second chain transmission mechanism includes a second driving wheel, a second guide wheel, a second driven wheel, a second fixed wheel, a second tensioning wheel shaft, a second tensioning wheel, and a second transmission chain, the second driving wheel is arranged on the transmission shaft, the second guide wheel is installed on the slider seat of the right column, the second guide wheel moves along the second transmission chain to drive the slider seat on the right column to slide on the right column, the second driven wheel is installed on the right column and is located below the slider seat, the second fixed wheel is installed on the motor mounting frame and is above the slider seat of the right column, the second tensioning wheel shaft is supported on the motor mounting frame and is located below the second fixed wheel side, the second tensioning wheel is installed on the second tensioning wheel shaft, and the second transmission chain is installed on the second driving wheel, the second guide wheel, the second driven wheel, the second fixed wheel, and the second tensioning wheel.

7. The test bench for automobile rollover collision test according to claim 1, characterized in that: It also includes a slide drive device, which includes a cylinder and a brake pad. A guide rail is provided on the base, and the slide slides on the base through the guide rail. The brake pad is arranged on the guide rail.

8. The test bench for automobile rollover collision test according to claim 7, characterized in that: When the slide drive device loads a sine wave to the slide, the slide launch moment expression is as follows: Where T1 is the launch time of the sine wave slide, v z is the vertical collision velocity of the test vehicle corresponding to the current test condition, a z is the vertical acceleration of the test vehicle collision corresponding to the current test condition, and σ is the period correction coefficient.

9. The test bench for automobile rollover collision test according to claim 7, characterized in that: When the slide drive device loads a trapezoidal wave to the slide, the slide launch time expression is as follows: Where T2 is the launch time of the trapezoidal wave slide, v z is the vertical collision velocity of the test vehicle corresponding to the current test condition, a z is the vertical acceleration of the test vehicle collision corresponding to the current test condition, v x is the collision velocity of the slide corresponding to the current test condition, a x is the slide collision velocity corresponding to the current test condition.

10. The test bench for automobile rollover collision test according to claim 1, characterized in that: During the test, the height between the slider seat and the slide table satisfies the following relationship: Where h is the height between the slider seat and the slide table, v is z is the vertical collision velocity of the test vehicle corresponding to the current test condition; a z It is the vertical acceleration of the test vehicle collision corresponding to the current test condition.

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