Testing device for vehicle ABS braking efficiency under vibration and rolling stone road surfaces

Abstract

The utility model relates to a testing device for vehicle ABS braking efficiency under vibration and rolling stone road surfaces, which comprises a testing stand and a rack, a roller assembly on the testing stand is provided with a front roller, a rear roller and a middle roller located between the front roller and the rear roller, bearings of the rollers are connected to a roller base frame through corresponding vertical sliding rails, and the middle roller is provided with a vertical sliding rail. The rack is provided with a rack groove capable of containing the test bench, a lifting jack used for supporting the test bench and capable of driving the test bench to vibrate is arranged between the bottom face of the test bench and the groove bottom of the rack groove, and an ejector rod used for ejecting the test bench from the front end is arranged between the front side of the test bench and the front side of the rack groove. A push rod used for pushing the test bench forwards is arranged between the rear side of the test bench and the rear wall of the rack groove. According to the utility model, road conditions such as rolling stone and vibration can be simulated so as to realize vehicle ABS braking efficiency detection under corresponding working conditions.

Description

Technical Field

[0001] This utility model relates to a testing device for the ABS braking performance of vehicles under vibration and gravel road conditions. It can be mainly used for testing or experimenting with the ABS braking performance of vehicles under corresponding hazardous conditions. Background Technology

[0002] Existing vehicle ABS braking test benches include roller assemblies that cooperate with the wheels. When the wheels rotate, they drive the rollers in the roller assembly to rotate. Inertial loads such as flywheels are placed on the rollers to simulate the vehicle's inertia. Braking is applied when the wheels reach a certain speed. Braking performance is obtained through analysis or calculation based on experimental data (e.g., braking time, load inertia, adhesion coefficient / friction coefficient, etc.). For example, Chinese patent document CN210802916U discloses a ramp ABS braking test bench, including a mounting plate. A ramp body is rotatably mounted on one end of the mounting plate. An adjustment mechanism is provided at the other end of the mounting plate and the ramp body. Four test components are mounted on the ramp body. A buffer mechanism is provided at the top of the ramp body. Two fixing mechanisms are used to fix and clamp the vehicle traveling on the four test components, while the adjustment mechanism adjusts and supports the angle of the ramp body. Chinese patent document CN106441922 discloses a bus ABS braking test bench device. A roller frame can move along a rack and pinion slide rail. The wheels drive the rollers through friction. An automatic water sprayer and a feeding mechanism are installed on the roller frame. A sand and gravel recovery device is installed at the lower end of the roller frame. A conveying device is installed between the feeding mechanism and the sand and gravel recovery device. The conveying device is driven by a motor, and the transmission belt has strip-shaped rubber protrusions. Chinese patent document CN218067038U discloses a ramp ABS braking test bench, including a base baffle. A ramp body is rotatably mounted on the top end of the base baffle. A buffer baffle is provided on the inner wall of the ramp body. A row of buffer springs is movably connected to the side wall adjacent to the base baffle and the buffer baffle. A driven groove is opened at the lower top end of the base baffle. A first sliding rod is horizontally installed on the inner wall of the driven groove. A docking groove and baffle assemblies are laid on the two sets of docking grooves at the upper opening of the active groove. Baffle assemblies are also laid at the upper openings of other active grooves. These existing technologies each have their own characteristics and are suitable for their respective occasions and experimental requirements, but they still cannot meet the various needs in practice. For example, the test bench itself is difficult to simulate road conditions such as gravel roads, bumpy (undulating) roads, and roads affected by earthquakes or flash floods, and cannot obtain braking performance under these conditions. Utility Model Content

[0003] The purpose of this invention is to simulate the working conditions of rolling stones (undulating) and vibrating road surfaces on the test bench, so as to enable the testing of vehicle ABS braking performance under the corresponding working conditions.

[0004] The technical solution of this utility model is: a test device for the ABS braking performance of vehicles under vibration and gravel road conditions, including a test bench. The test bench is provided with multiple roller assemblies (measurement and control units) corresponding to the wheels. Each roller assembly is provided with a first roller, which includes a front roller and a rear roller. The roller assembly is also provided with a second roller, which is a middle roller located between the front roller and the rear roller. The bearings (or bearing supports) of the front roller, the middle roller, and the rear roller are all connected to the roller base frame (the base frame of the roller assembly) through corresponding vertical (perpendicular to the top surface of the test bench) slide rails (vertical linear guide mechanisms). The vertical slide rails are provided with vertical drive mechanisms for driving the sliding parts of the vertical slide rails to move vertically.

[0005] The bearings (bearing outer rings or bearing housings) of each roller (front roller, rear roller, and middle roller) can be set / installed on the sliding parts (e.g., sliders) of the corresponding vertical slide rails, and the fixing parts (e.g., grooves) of the vertical slide rails can be installed on the roller base frame. The vertical drive mechanism can be a hydraulic cylinder (or pneumatic cylinder) or a screw and nut mechanism with a drive motor, thereby realizing the vertical movement and fixation of the corresponding bearings.

[0006] When the bearings on both sides of the same roller are respectively equipped with their own vertical slide rails, the slide rail drive mechanism for driving the same roller can be one, and its drive output component (e.g., the outer end of the piston rod of the hydraulic cylinder) is connected to the sliding component of the vertical slide rail on either side (including the bearing seat of the corresponding bearing or the drive connecting plate and other components / structures fixedly connected to the sliding component); the slide rail drive mechanism for driving the same roller can also be two, and the drive output components of the two slide rail drive mechanisms are respectively connected to the sliding component of their respective vertical slide rails. The two drive mechanisms move synchronously, thereby driving the slide rail sliding components on both sides of the roller to move synchronously.

[0007] Preferably, the first roller is connected to the first inertial load via a first transmission mechanism (e.g., a bevel gear set with two synchronous input ends), the first transmission mechanism having two synchronous input ends, which are respectively connected to the rotating shafts of the front roller and the rear roller (e.g., connected via a coupling), and the second roller is connected to the second inertial load via a second transmission mechanism.

[0008] Preferably, the first and second transmission mechanisms have the same transmission ratio. However, they may differ when appropriate. A coupling used to achieve direct connection between two shaft ends (e.g., a flange connection structure) is considered a transmission mechanism with a transmission ratio of 1.

[0009] Preferably, the first inertial load and the second inertial load take the same form, for example, a flywheel.

[0010] Data on the rollers (e.g., rotational speed, time to stop rotation, etc., for example, by setting up corresponding sensors) can be detected using existing technologies and analyzed and processed.

[0011] Preferably, this testing device also includes a frame, which is trough-shaped and has a slot to accommodate the test bench (with clearance to allow the test bench to tilt and move as needed, but the clearance should generally be kept from being too large and affecting the stability of the test bench). A lifter is provided between the bottom surface of the test bench and the bottom of the slot to support the test bench and to drive the test bench to vibrate. A push rod (lifting rod mechanism, or lifting push rod) is provided between the front side of the test bench and the front side of the slot to lift the test bench from the front end (and allows / can return to its original position). A push rod (push rod mechanism, or lifting push rod) is provided between the rear side of the test bench and the rear wall of the slot to push the test bench forward (and allows / can return to its original position).

[0012] Preferably, the upper and lower ends of the lifter are hinged to the bottom surface (lower surface) of the test bench and the bottom of the frame slot, respectively (e.g., directly hinged to the bottom of the slot via a suitable hinge / hinged pair, or hinged to other parts fixed or movably connected to the bottom of the slot via a suitable hinge), the upper and lower ends of the push rod are hinged to the front side of the test bench (e.g., the near front end of the bottom surface of the test bench) and the front side of the frame slot (e.g., the front wall of the frame slot), respectively, and the front and rear ends of the push rod are hinged to the rear end of the test bench (e.g., the rear end face of the test bench) and the rear wall of the frame slot, respectively.

[0013] Typically, the push rod extends horizontally in the longitudinal (front-to-back) direction to facilitate horizontal movement of the test bench. When the test bench is tilted forward or backward, the push rod can tilt slightly with the test bench.

[0014] Preferably, both the push rod and the ejector rod are hydraulic cylinders (including commonly referred to as oil cylinders and pneumatic cylinders). The overall extension and retraction of the push rod and ejector rod are achieved through the action of the hydraulic cylinder. The stroke and length of the hydraulic cylinder piston rod are set according to actual needs. For example, the length of the piston rod can be increased based on the original piston rod of a commercially available standard hydraulic cylinder (for example, by adding a rod section) to meet the length requirements of the push rod. During installation, the bottom of the hydraulic cylinder body (rodless end) can be connected to the frame slot as the lower end of the push rod or the rear end of the ejector rod, and the front end of the piston rod can be connected to the test bench as the upper end of the push rod or the front end of the ejector rod.

[0015] Preferably, the upper end of the push rod is hinged to the front side of the test platform using an elastic ball joint, with the upper end of the push rod connected to the ball head of the elastic ball joint and the front side of the test platform connected to the ball socket (slipper) of the corresponding elastic ball joint; the front end of the push rod is hinged to the rear end of the test platform using an corresponding elastic ball joint, with the front end of the push rod connected to the ball head of the corresponding elastic ball joint and the rear end of the test platform connected to the ball socket of the corresponding elastic ball joint.

[0016] Furthermore, an elastic pad is provided between the ball head and the socket of the elastic ball joint, thereby relying on the deformation of the elastic pad to achieve relative displacement between the ball head and the socket. The elastic pad conforms to the shape of the socket and fills the space between the ball head and the socket.

[0017] The number of top rods can typically be multiple, distributed at different positions in the lateral direction (e.g., at least at both ends in the lateral direction) to achieve balanced / stable support for the test bench.

[0018] The number of push rods can be one or more. When there are multiple push rods, they can usually be arranged symmetrically from left to right. When there is only one push rod, it can be set in the center of the horizontal direction to achieve balanced thrust.

[0019] Preferably, the lifter is a hydraulic cylinder, and the overall extension and retraction of the lifter is achieved by the movement of the hydraulic cylinder. The stroke and length of the piston rod of the hydraulic cylinder are set according to actual needs. The bottom of the cylinder body (rodless end) can be connected to the bottom of the frame slot (or the sliding part of the longitudinal slide rail set at the bottom of the slot) as the lower end of the lifter, and the front end of the piston rod can be connected to the bottom surface of the test bench as the upper end of the lifter.

[0020] Preferably, the bottom of the frame slot is provided with a longitudinal slide rail (a longitudinal linear guide mechanism, or a lifter slide rail), and the lower end of the lifter is hinged to the sliding member of the corresponding longitudinal slide rail, thereby achieving hinge connection with the bottom of the slot.

[0021] The upper end of the lift (e.g., the upper end of the corresponding cylinder piston rod) can be connected to a hinge (e.g., the ball head of a ball joint) via an elastic connector (e.g., a leaf spring or a coil spring).

[0022] The number of lifters is usually multiple, preferably symmetrically distributed left and right and front and back. Lifters should typically be installed on both sides laterally and at both ends longitudinally. Through the cooperation of the lifters, push rods, and jacks, balanced and stable support for the test bench is achieved. For example, when the test bench is level, it can be supported by the individual lifters.

[0023] The beneficial effects of this utility model are as follows: Because a middle roller is included in the roller assembly, and each roller can move up and down via vertical slide rails, the middle roller can be positioned higher than the front and rear rollers, forming a convex shape in the middle, or lower than the front and rear rollers, forming a concave shape in the middle. Through alternating convex and concave shapes, it can effectively simulate road surfaces such as gravel roads, bumpy roads, and road surface vibrations caused by severe environments such as earthquakes and floods. Because a lifter capable of vibrating the test bench is included, it can effectively simulate road surface vibrations or vibration-like effects caused by severe environments such as earthquakes or floods. Because a top rod and a push rod are included, the test bench can be tilted under the synergistic action of the top rod and push rod, effectively simulating tilted road surfaces. Because the lifter and test bench are hinged, and a longitudinal slide rail is provided between the lifter and the frame, the lifter can appropriately change its position and attitude as the test bench tilts, ensuring that the lifter can still effectively vibrate the test bench even when it is tilted. Because the lifter... The upper end of the device can be equipped with elastic connectors, which can achieve buffering near the highest and lowest points (the highest and lowest points during the vibration of the lifter), reduce the load capacity requirements of the lifter, and better simulate the ground vibration state. Since the connection between the top rod and push rod and the test bench can be made with elastic ball joints, it is beneficial to realize the vibration of the test bench while ensuring the action of the top rod and push rod on the test bench, and it is beneficial to reduce the impact of vibration on the top rod and push rod and the connection structure between them and the test bench, thus extending their service life. Since there can be multiple top rods, it is not only beneficial to balance and stability, but also allows different top rods to use different lengths, which can better simulate the lateral tilt of the road surface. Since there can be one or more rear top rods, and the rear top rods are connected to the test bench and the frame with ball joints, they can cooperate with the top rods to realize a certain degree of lateral tilt of the test bench. Since the front roller and the rear roller are connected to the same bevel gear set, it is beneficial to ensure the synchronous and uniform rotation of the front and rear rollers through the bevel gear set. Attached Figure Description

[0024] Figure 1 This is a schematic diagram illustrating the state change principle of the detection device involved in this utility model;

[0025] Figure 2 This is a schematic diagram of the detection device involved in this utility model in a planar (folded) state;

[0026] Figure 3 This is a schematic diagram of the horizontal lifting state of the detection device involved in this utility model;

[0027] Figure 4 This is a schematic diagram of the tilted state of the detection device involved in this utility model;

[0028] Figure 5 This is a schematic diagram (top view) of the test bench involved in this utility model;

[0029] Figure 6 This is a schematic diagram (top view) of the roller assembly involved in this utility model.

[0030] Figure 7 This is a schematic diagram (side view) showing the vertical relative positions of the first roller and the second roller in the roller assembly involved in this utility model.

[0031] Figure 8 This is a schematic diagram (end face) of the roller assembly involved in this utility model.

[0032] Figure 9 This is a schematic diagram of the convex / concave / undulation formed by the roller assembly (with the middle roller being relatively convex);

[0033] Figure 10 This is a schematic diagram of the convex / concave / undulation formed based on the roller assembly (the middle roller is relatively concave);

[0034] Figure 11 This is a schematic diagram of the elastic ball joint involved in this utility model.

[0035] The markings in the diagram are: 1. Frame; 2. Test bench; 201. Roller base frame; 202. Front roller; 203. Middle roller; 204. Rear roller; 205. First bearing; 206. Second bearing; 207. Second inertial load; 208. First inertial load; 209. First transmission mechanism; 210. Vertical slide rail; 211. Ball head; 212. Ball socket; 213. Elastic pad; 214. Elastic connector; 3. Locking device; 4. Lifter; 5. Longitudinal slide rail; 6. Top rod; 7. Push rod. Detailed Implementation

[0036] See Figures 1 to 11 This testing device has a slotted frame 1 and a test bench 2. Both the slot on the frame and the test bench are rectangular. The width and length of the slot are slightly larger than the test bench to allow the test bench to move and rotate relative to the frame, and a gap is provided to allow for rotation.

[0037] The test bench can adopt a structure that is roughly the same as that of existing related test benches. It is usually equipped with four roller assemblies (or test assemblies or test units) corresponding to the four wheels of the vehicle. During testing, the vehicle is placed on the test bench, and the four wheels press on the four roller assemblies respectively. When the wheels rotate, they drive the rollers to rotate. By detecting the roller data during the braking process, the braking performance of the vehicle can be analyzed / calculated.

[0038] The roller assembly includes a first roller, which comprises a front roller 202 and a rear roller 204. A second roller is added to the first roller, which is a middle roller 203 located between the front roller and the rear roller. The bearings of each roller (including the first bearing 205 of the first roller and the second bearing 206 of the second roller) are connected to the roller base frame (base frame of the roller assembly) 201 through their respective vertical slide rails (longitudinal linear guide mechanisms) 210. The vertical slide rails are provided with vertical drive mechanisms for driving the sliding members of the vertical slide rails to move vertically.

[0039] A top rod 6, a push rod 7, and a lifter 4 are installed between the frame and the test bench. The top rod lifts the front end of the test bench, while the push rod pushes the test bench forward and pulls it backward. Together with the top rod, they maintain the test bench in a suitable tilt position and enable it to reciprocate (longitudinal vibration) to simulate or assist in simulating dangerous conditions such as earthquakes. The lifter works in conjunction with the top rod and push rod to support the test bench and drive its vertical vibration. A longitudinal slide rail 5 is installed at the lower end of the lifter, allowing the lifter to adjust its posture by longitudinal movement at the lower end to ensure the vibration direction. If necessary, existing technology can be used to install an electromagnetic locking device between the sliding and fixed parts on the longitudinal slide rail. After the lifter's posture is adjusted, the position of the sliding part is locked, thereby locking the longitudinal position of the lower end of the lifter and the lifter's posture.

[0040] A suitable hinge structure (hinged pair) can be used to achieve the hinge between the relevant components. For example, the upper end of the push rod is hinged to the front side of the test platform using an elastic ball joint, with the upper end of the push rod connected to the ball head of the elastic ball joint and the front side of the test platform connected to the corresponding ball socket (slipper) of the elastic ball joint; the front end of the push rod is hinged to the rear end of the test platform using a corresponding elastic ball joint, with the front end of the push rod connected to the ball head of the corresponding elastic ball joint and the rear end of the test platform connected to the corresponding ball socket of the elastic ball joint. An elastic pad 213 is provided between the ball head 211 and the ball socket 212 of the elastic ball joint.

[0041] The upper end of the lift (e.g., the upper end of the corresponding cylinder piston rod) can be connected to a hinge (e.g., the ball joint of a ball joint) via a resilient connector (e.g., a leaf spring or a coil spring) 214.

[0042] The inertial load of the rollers can be set according to actual needs, for example, a flywheel. The inertial load simulates the vehicle's inertia during braking. For example, the first roller is connected to the first inertial load 208 via a first transmission mechanism (e.g., a bevel gear set with two synchronous input ends) 209. The first transmission mechanism has two synchronous input ends, which are respectively connected to the shafts of the front roller and the rear roller (e.g., connected via couplings). The second roller is connected to the second inertial load 207 via a second transmission mechanism. Normally, the transmission ratios of the first and second transmission mechanisms are the same, but they can be different when appropriate.

[0043] A locking device 3 can be installed between the test bench and the frame. The locking device can be a folded rod structure consisting of multiple rods connected end to end in sequence. One end is connected to the rear of the test bench (for example, by bolts and a connecting structure matching the bolts), and the other end is connected to the rear of the frame to limit the maximum forward movement of the test bench.

[0044] This invention can be used for the following tests:

[0045] 1) Braking test on level roads:

[0046] It includes two scenarios: completely flat road detection and flat road bump detection.

[0047] The test bench is horizontal, with its top surface aligned with or higher than the top surface of the frame (corresponding to fully level road testing and level road bump testing, respectively). The top rod and push rod are retracted or removed (disconnected), and the lifter is vertical, supporting the test bench. No vertical or forward / backward vibration is applied. Road bumps (the middle roller moves up to contact the wheel or lifts the wheel) or bump / concave changes are applied or not, in conjunction with different types of vehicles entering and leaving the test bench, to perform testing under corresponding working conditions.

[0048] 2) Hill Start Braking Test:

[0049] It includes three scenarios: simple slope detection, slope bulge detection, and slope vibration detection.

[0050] The test bench is pushed to the required ramp angle by the push rod and is independently connected to the measurement and control unit. The push rod acts as a support to lift the test bench, controlling the position of the corresponding sliding parts in the longitudinal slide rail (a longitudinal drive mechanism can be set to drive the movement of the sliding parts of the longitudinal slide rail, such as a longitudinal drive cylinder or a longitudinal screw and nut mechanism with a drive motor) and the length of the lifter, so that the lower end of the lifter slides to the corresponding position of the longitudinal slide rail. Vertical vibration and / or longitudinal vibration are implemented through the lifter and / or push rod as needed, or no vibration is implemented, to simulate the corresponding ramp vibration or static state, and to carry out the test under the corresponding working conditions.

[0051] 3) Vibration detection on level roads

[0052] It includes two working conditions: simple vibration on flat roads and vibration on flat roads with bulges.

[0053] The test bench is horizontal (its top surface is aligned with or higher than the top surface of the frame), and the push rod and push rod are in a retracted or disassembled (disconnected) state. Vertical vibration and / or longitudinal vibration are implemented through the lift and / or push rod as needed to carry out testing under corresponding working conditions.

[0054] The test conditions can be set according to actual needs.

[0055] For example, in one embodiment, based on a driver in a hilly city encountering a minor landslide, the vehicle's braking performance under subconscious braking conditions was tested. The specific conditions were: road slope of 5°, earthquake frequency of 5-20Hz, and occasional falling rocks on the road surface.

[0056] The adhesion coefficient of each wheel is set according to the test requirements, i.e., the rollers are made of different materials. The car drives onto the test bench, so that the wheels contact the corresponding front and rear rollers. The vehicle is started and driven at low speed to straighten the wheels and fix the body to prevent it from rolling out. The control rod lifts the front end of the test bench at a 5° angle, and the lower end of the lifter slides to the corresponding position on the longitudinal slide rail, so that the extension direction (or axial direction) of the lifter is perpendicular (basically perpendicular) to the test bench (top surface).

[0057] During the test, the lifter extended and retracted at a frequency of 5 Hz to simulate ground vibration. The front and rear rollers and the middle roller moved up and down (perpendicular to the road surface) with a difference of 30 mm based on the vertical slide rail (and its drive mechanism) to simulate the obstruction of the wheels by falling rocks.

[0058] During testing, the vehicle is started, and the wheels drive the rollers to rotate. Once the vehicle has coasted at 40 km / h, emergency braking is applied until the vehicle speed reaches zero. Based on data collected during braking, including roller speed (speed change), distance traveled (the distance the vehicle travels based on wheel rotation), braking time, and the coefficient of dynamic friction of the selected roller material, the vehicle's adhesion coefficient utilization rate, vehicle slip ratio relative to the ground, and braking performance are calculated to evaluate the vehicle's ABS system performance.

[0059] This invention can be widely used to simulate the ABS performance testing of vehicles in areas prone to various geological disasters (such as vehicle testing in areas with heavy rainstorms and flash floods, and vehicle testing under various dangerous conditions during disaster relief work). It can test the braking performance of vehicles when drivers brake in emergency situations on special dangerous road surfaces in different cities and regions. It can not only detect the impact of external forces on the entire test as much as possible, but also benefit ABS research and development, rally vehicle inspection, and teaching of vehicle-related majors.

[0060] Unless otherwise specified, the preferred and optional technical means disclosed in this utility model can be arbitrarily combined to form several different specific embodiments when one preferred or optional technical means is a further limitation of another technical means.

Claims

1. A test device for testing the ABS braking performance of a vehicle on a road surface with shaking and rolling stones, comprising a test bed, a plurality of drum assemblies corresponding to wheels are arranged on the test bed, each drum assembly is provided with a first drum, and the first drum comprises a front drum and a rear drum, characterized in that The roller assembly is further provided with a second roller, which is a middle roller between the front roller and the rear roller, and the bearings of the front roller, the middle roller and the rear roller are connected to a roller base frame through corresponding vertical slide rails, and the vertical slide rails are provided with vertical driving mechanisms for driving the sliding members of the vertical slide rails to move vertically.

2. The test device of claim 1, wherein The first roller is connected to a first inertial load through a first transmission mechanism, and the first transmission mechanism is provided with two synchronous input ends connected to the rotating shafts of the front roller and the rear roller respectively.

3. The test device of claim 2, wherein The transmission ratios of the first transmission mechanism and the second transmission mechanism are the same.

4. The test device of claim 2, wherein The first inertial load and the second inertial load adopt the same form.

5. The test device of claim 1, wherein A rack is further provided, which is in a groove shape and is provided with a rack groove capable of accommodating the test table, and a lifter for supporting the test table and capable of driving the test table to vibrate is arranged between the bottom surface of the test table and the groove bottom of the rack groove, a jacking rod for jacking the test table from the front end is arranged between the front side of the test table and the front side of the rack groove, and a pushing rod for pushing the test table forward is arranged between the rear side of the test table and the rear wall of the rack groove.

6. The test device of claim 5, wherein The upper end and the lower end of the lifter are respectively hinged to the bottom surface of the test table and the groove bottom of the rack groove, the upper end and the lower end of the jacking rod are respectively hinged to the front side of the test table and the front side of the rack groove, and the front end and the rear end of the pushing rod are respectively hinged to the rear end of the test table and the rear wall of the rack groove.

7. The test device of claim 5, wherein The jacking rod and the pushing rod both adopt oil cylinders.

8. The test device of claim 5, wherein The upper end of the jacking rod is hinged to the front side of the test table through an elastic ball hinge, the upper end of the jacking rod is connected to the ball head of the elastic ball hinge, and the front side of the test table is connected to the ball socket of the corresponding elastic ball hinge; the front end of the pushing rod is hinged to the rear end of the test table through a corresponding elastic ball hinge, the front end of the jacking rod is connected to the ball head of the corresponding elastic ball hinge, and the rear end of the test table is connected to the ball socket of the corresponding elastic ball hinge.

9. The test device of claim 5, wherein The lifter adopts an oil cylinder.

10. The test device of claim 5, wherein The groove bottom of the rack groove is provided with a longitudinal slide rail, and the lower end of the lifter is hinged to the sliding member of the corresponding longitudinal slide rail, thereby realizing the hinging to the groove bottom.

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