Passenger car air spring vertical durability loading test device

Abstract

The utility model relates to the technical field of air suspension system performance testing, and discloses a passenger car air spring vertical endurance loading test device, which comprises a driving assembly, a triangular arm, a loading rod and a mounting seat, a right-angle end, a first side edge and a second side edge are formed on the triangular arm, and the triangular arm is configured to rotate by taking the right-angle end as a center; one end of the driving assembly is hinged to the mounting base, and the other end of the driving assembly is movably connected with the first side edge; the driving assembly is configured to do telescopic motion in the horizontal direction, and the driving assembly can pull the first side edge in the telescopic process so that the triangular arm can rotate with the right-angle end as the center; one end of the loading rod is used for being connected with an air spring, the other end of the loading rod is movably connected with the second side edge, the loading rod is arranged in the vertical direction, and the triangular arm can drive the loading rod to move in the vertical direction in the rotating process. According to the utility model, the conversion from horizontal driving to vertical loading is realized through the triangular arm, the occupied space is obviously reduced, and the manufacturing cost is reduced.

Description

Technical Field

[0001] The utility model relates to the technical field of air suspension system performance testing, in particular to a vertical durability loading test device for an air spring of a passenger car. Background Art

[0002] With the rapid development of the automotive industry, the design and optimization of air suspension systems have become crucial for enhancing the driving experience and vehicle performance. As the core component of an air suspension system, air springs utilize the reaction force generated by the internal compression of the rubber bladder as a restoring force, providing shock absorption and dynamic stability for the vehicle. However, the performance and durability of air springs are directly linked to the design and craftsmanship of their bladder casings, which in turn determines the overall service life of the air spring. Consequently, durability testing is crucial in the development and production of air springs.

[0003] In traditional air suspension systems, air spring performance testing often relies on complex testing equipment. This is especially true for vertical loading, which requires the construction of large gantry systems or sophisticated support structures to simulate the load variations experienced in actual operating conditions. These devices are not only expensive, but also require significant floor space and are complex to install and debug. Utility Model Content

[0004] The purpose of the utility model is to provide a vertical durability loading test device for passenger car air springs, so as to solve the problem that traditional air spring performance test devices need to construct a gantry system or a supporting structure, which is relatively costly.

[0005] In order to achieve the above purpose, the technical solution adopted by the present utility model is as follows:

[0006] A vertical durability loading test device for a passenger car air spring comprises: a drive assembly, a triangular arm, a loading rod and a mounting seat, wherein the triangular arm is formed with a right-angle end, a first side and a second side, and the triangular arm is configured to be able to rotate around the right-angle end; one end of the drive assembly is hinged on the mounting seat, and the other end of the drive assembly is movably connected to the first side; the drive assembly is configured to be able to perform telescopic movement in the horizontal direction, and the first side can be pulled during the telescopic process of the drive assembly to rotate the triangular arm around the right-angle end; one end of the loading rod is used to connect to the air spring, and the other end of the loading rod is movably connected to the second side, and the loading rod is arranged in the vertical direction, and can drive the loading rod to move in the vertical direction during the rotation of the triangular arm to stretch or squeeze the air spring.

[0007] Based on the above-mentioned technical means, the present invention achieves an efficient conversion from horizontal drive to vertical loading through a triangular arm. Specifically, the drive assembly telescopes in the horizontal direction, and the triangular arm can rotate with its right-angle end as a fulcrum, thereby converting the horizontal force of the drive assembly into vertical movement of the loading rod, simplifying the loading path and improving the efficiency of energy conversion. Furthermore, by converting the loading direction, the triangular arm in the present invention avoids the need for complex gantry or other support structures required in traditional vertical loading methods, thereby significantly reducing space usage and manufacturing costs.

[0008] Due to the rotating nature of the triangular arm, the triangular arm in this utility model can flexibly adjust the vertical position of the loading rod according to the loading requirements, making the test device easily adaptable to the testing requirements of different air springs, including those with different sizes, different installation heights, and different loading ranges. Furthermore, by adjusting the extension and retraction of the drive assembly, the vertical movement distance of the loading rod can be further precisely controlled, achieving more refined loading control.

[0009] Furthermore, it also includes a first movable connection component, and the other end of the driving component is movably connected to the first side through the first movable connection component.

[0010] According to the above technical means, when the jib arm rotates, the first side moves along a circular arc. If a rigid connection is used, one end of the drive assembly will be subjected to a large lateral force, which may cause the connection to fail or be damaged. The utility model adopts the design of the first movable connection component, which allows a certain amount of movable space or freedom between the drive assembly and the first side of the jib arm. This allows the drive assembly to drive the jib arm to rotate more smoothly during the extension and retraction process, reducing the friction and resistance caused by the rigid connection, and improving operating efficiency.

[0011] Furthermore, the first movable connection component includes a first joint bearing and a first articulated seat, the first joint bearing is installed on the driving component, the first articulated seat is installed on the first side, and the first joint bearing is hinged to the first articulated seat so that the driving component is hinged to the triangular arm.

[0012] According to the above technical means, the first spherical bearing is capable of multi-directional rotation and swinging within a certain range, allowing it to effectively adapt to the displacement and angular changes caused by the rotation of the yoke. The first articulated seat is mounted on the first side of the yoke, corresponding to the first spherical bearing. The first spherical bearing and the first articulated seat are articulated through spherical contact. When the drive assembly performs telescopic movement, it transmits force to the first articulated seat through the first spherical bearing, thereby driving the yoke to rotate about the right-angle end.

[0013] Furthermore, a first mounting hole is formed on the first hinge seat, and a plurality of second mounting holes are formed on the first side, and the second mounting holes are evenly distributed along the length direction of the first side; the first mounting hole is adapted to the second mounting holes so that the first hinge seat can be installed on the first side.

[0014] According to the above technical means, the cooperation between the first mounting hole formed on the first articulated seat and the multiple second mounting holes formed on the first side in the present invention is not only used to fix the position of the first articulated seat on the triangular arm, but also can achieve different transmission ratios by selecting appropriate hole positions. Different second mounting hole positions correspond to different lever arm lengths (i.e., the distance from the first articulated seat to the rotation center point of the triangular arm). A longer lever arm can produce a larger input torque; a shorter lever arm may produce a smaller input torque. The present invention can adjust the lever arm length by selecting appropriate hole positions, thereby adjusting the swing amplitude and path of the triangular arm during the rotation process, so as to better simulate the vertical loading conditions in actual working conditions.

[0015] Furthermore, it also includes a second movable connection component, and the other end of the loading rod is movably connected to the second side through the second movable connection component.

[0016] According to the above technical means, similar to the first movable connection assembly, the second movable connection assembly ensures the flexibility between the loading rod and the triangular arm. The loading rod can move or rotate to a certain extent relative to the triangular arm during the vertical loading process to adapt to the deformation of the air spring during the loading process and reduce the stress concentration and damage risk caused by the rigid connection.

[0017] Furthermore, the second movable connection assembly includes a second joint bearing and a second articulated seat, the second joint bearing is installed on the loading rod, the second articulated seat is installed on the second side, and the second joint bearing is hinged to the second articulated seat so that the loading rod is hinged to the triangular arm.

[0018] According to the aforementioned technical approach, the second spherical bearing can accommodate various angle and displacement changes that may occur between the loading rod and the yoke during loading. A second articulated seat is mounted on the second side of the yoke, corresponding to the second spherical bearing. The second spherical bearing and the second articulated seat are articulated via spherical contact. When the loading rod is subjected to a vertical loading force, the force is transmitted to the second articulated seat via the second spherical bearing, thereby driving the yoke to rotate about the right-angle end.

[0019] Furthermore, a third mounting hole is formed on the second hinged seat, and a plurality of fourth mounting holes are formed on the second side, and the fourth mounting holes are evenly distributed along the length direction of the second side; the third mounting hole is adapted to the fourth mounting holes so that the second hinged seat can be installed on the second side.

[0020] Based on the above technical means, the three mounting holes formed on the second hinge base and the multiple fourth mounting holes formed on the second side of the present invention not only fix the position of the second hinge base on the yoke, but also enable different transmission ratios to be achieved by selecting appropriate hole positions. Different fourth mounting hole positions correspond to different lever arm lengths (i.e., the distance from the second hinge base to the rotation center of the yoke).

[0021] Furthermore, it also includes a rotating assembly, the right-angle end of the triangular arm is connected to the rotating assembly, and the rotating assembly is used to rotatably support the triangular arm on the ground.

[0022] According to the above technical means, the rotating assembly provides a stable support point for the triangular arm, ensuring that the triangular arm can maintain a stable posture during the loading process and avoid shaking or tilting.

[0023] Furthermore, the rotating assembly includes a base, a bearing and a rotating shaft, the base is used to support the ground; the bearing is mounted on the base, and the rotating shaft is rotatably mounted on the bearing; a fifth mounting hole is formed on the right-angle end, the fifth mounting hole is adapted to the rotating shaft, and the rotating shaft can pass through the fifth mounting hole to rotatably mount the triangular arm on the bearing.

[0024] Using these technical measures, the base is firmly supported on the ground, providing a stable foundation for the jib. Bearings mounted on the base effectively reduce friction and wear, allowing the shaft to rotate smoothly with low resistance. The design of the rotating assembly ensures that the jib maintains a stable posture during loading, preventing shaking or tilting that could affect the accuracy of test results.

[0025] Furthermore, it also includes an insulation box and an insulation box bracket, and the air spring is fixed in the insulation box; the insulation box is arranged above the loading rod through the insulation box bracket, and at least part of the loading rod extends into the insulation box to connect with the air spring.

[0026] According to the above technical means, the insulation box is used to maintain the stability of the internal temperature. In the durability test of the air spring, temperature is an important influencing factor. The insulation box can be used to simulate the working environment under different temperature conditions to evaluate the performance of the air spring at different temperatures. At the same time, the insulation box can also effectively isolate the interference of the external environment on the test, such as temperature fluctuations, humidity changes, dust pollution, etc., which helps to reduce test errors and improve the accuracy of test results. The insulation box bracket is used to firmly support the insulation box above the loading rod, which not only ensures the stability of the insulation box, but also enables the loading rod to be accurately connected to the air spring in the insulation box.

[0027] Beneficial effects achieved by this utility model:

[0028] 1. This utility model achieves efficient conversion from horizontal drive to vertical loading through a triangular arm. Specifically, the drive assembly telescopes horizontally, and the triangular arm rotates with its right-angle end as a fulcrum, thereby converting the horizontal force of the drive assembly into vertical movement of the loading rod, simplifying the loading path and improving energy conversion efficiency. Furthermore, by switching the loading direction, the triangular arm in this utility model avoids the need for complex gantry or other support structures required in traditional vertical loading methods, significantly reducing space usage and manufacturing costs.

[0029] 2. Due to the rotating nature of the triangular arm, the triangular arm in this utility model can flexibly adjust the vertical position of the loading rod according to the loading requirements, making the test device easily adaptable to the testing requirements of different air springs, including those with different sizes, different installation heights, and different loading ranges. Furthermore, by adjusting the extension and retraction of the drive assembly, the vertical movement distance of the loading rod can be further precisely controlled, achieving more refined loading control. BRIEF DESCRIPTION OF THE DRAWINGS

[0030] Figure 1 It is a schematic diagram of the overall structure of the utility model;

[0031] Figure 2 This is a schematic diagram of the assembly structure of the utility model;

[0032] Figure 3 This is a schematic diagram of the connection structure of the triangular arm, the first hinge seat, the second hinge seat and the rotating assembly of the present invention;

[0033] Figure 4 for Figure 3 AA cross-sectional structural diagram;

[0034] Figure 5 This is a schematic diagram of the structure of the insulation box bracket of the utility model;

[0035] Figure 6This is a schematic diagram of the back plate of the thermal insulation box of the present invention;

[0036] Figure 7 This is a schematic diagram of the bottom plate of the thermal insulation box of the present invention;

[0037] Figure 8 This is a schematic diagram of the front plate of the thermal insulation box of the present invention;

[0038] Figure 9 This is a schematic structural diagram of the first movable connection assembly of the present utility model;

[0039] Among them, 1- drive component;

[0040] 2-triangular arm, 21-right angle end, 22-first side, 221-second mounting hole, 23-second side, 231-fourth mounting hole;

[0041] 3- Loading rod;

[0042] 4-Mounting seat;

[0043] 5-first movable connection assembly, 51-first joint bearing, 511-connecting column, 512-outer spherical end, 513-inner spherical end, 52-first hinge seat, 521-first mounting hole;

[0044] 6-second movable connection assembly, 61-second hinge seat, 611-third mounting hole;

[0045] 7-rotating assembly, 71-base, 711-iron floor connecting plate, 712-mounting base plate, 713-bearing seat, 72-bearing, 721-bearing body, 722-bearing end cover, 723-bearing baffle, 724-bearing baffle ring, 73-rotating shaft;

[0046] 8-insulation box, 81-back plate, 811-sixth mounting hole, 82-bottom plate, 821-through hole, 83-front plate, 831-observation window;

[0047] 9-insulation box bracket, 91-crossbeam, 92-second pad;

[0048] 10- pillar;

[0049] 11- first pad;

[0050] 12-Suspension mounting base plate.

[0051] The accompanying drawings are for illustrative purposes only and should not be construed as limitations on this patent. To better illustrate this embodiment, some components of the accompanying drawings may be omitted, enlarged, or reduced in size and do not represent the actual dimensions of the product. For those skilled in the art, it is understandable that some well-known structures and their descriptions may be omitted from the accompanying drawings. The same or similar reference numerals correspond to the same or similar components. The terms describing positional relationships in the accompanying drawings are for illustrative purposes only and should not be construed as limitations on this patent. DETAILED DESCRIPTION

[0052] It should be noted that, unless there is a conflict, the embodiments in this application and the technical features in the embodiments can be combined with each other. The detailed description in the specific embodiments should be understood as an explanation of the purpose of this application and should not be regarded as an improper restriction on this application.

[0053] To make the purpose, technical solutions and advantages of the embodiments of the present application clearer, the specific technical solutions of the present application will be further described in detail below in conjunction with the drawings in the embodiments of the present application. The following embodiments are used to illustrate the present application but are not intended to limit the scope of the present application.

[0054] In the embodiments of this application, the terms "first" and "second" are used for descriptive purposes only and should not be understood as indicating or implying relative importance or implicitly indicating the number of the technical features indicated. Therefore, a feature defined as "first" or "second" may explicitly or implicitly include one or more of the features. In the description of the embodiments of this application, unless otherwise specified, "multiple" means two or more.

[0055] In the embodiments of the present application, unless otherwise clearly specified and limited, the term "connection" should be understood in a broad sense. For example, "connection" can be a fixed connection, a detachable connection, or an integrated connection; it can be a direct connection or an indirect connection through an intermediate medium.

[0056] In the embodiments of the present application, the terms "comprises," "comprising," or any other variations thereof are intended to encompass non-exclusive inclusion, such that a process, method, article, or apparatus comprising a series of elements includes not only those elements but also other elements not explicitly listed, or elements inherent to such process, method, article, or apparatus. In the absence of further limitations, an element defined by the phrase "comprising a ..." does not preclude the presence of other identical elements in the process, method, article, or apparatus comprising the element.

[0057] The technical solution of this embodiment is described in detail below with reference to the specific drawings.

[0058] like Figure 1 and Figure 2As shown, this embodiment proposes a vertical endurance loading test device for passenger car air springs, comprising: a drive assembly 1, a triangular arm 2, a loading rod 3 and a mounting seat 4. Figure 3 As shown, a right-angle end 21, a first side 22 and a second side 23 are formed on the triangular arm 2, and the triangular arm 2 is configured to be able to rotate around the right-angle end 21; one end of the driving component 1 is hinged on the mounting seat 4, and the other end of the driving component 1 is movably connected to the first side 22; the driving component 1 is configured to be able to perform telescopic movement in the horizontal direction, and the driving component 1 can pull the first side 22 during the telescopic process to make the triangular arm 2 rotate around the right-angle end 21; one end of the loading rod 3 is used to connect the air spring, and the other end of the loading rod 3 is movably connected to the second side 23, and the loading rod 3 is arranged in the vertical direction. During the rotation of the triangular arm 2, the loading rod 3 can be driven to move in the vertical direction to stretch or squeeze the air spring.

[0059] During the test, the passenger car air spring durability vertical loading test apparatus was installed on a stable test platform, ensuring that the mounting base 4 remained stationary to provide stable support. The air spring to be tested was mounted to one end of the loading rod 3 according to the design requirements, ensuring a secure and reliable connection. Under no-load conditions, the drive assembly 1 was activated and subjected to several reciprocating telescopic movements. The smooth rotation of the triangular arm 2 and the smooth vertical movement of the loading rod 3 were observed to calibrate the mechanical performance of the entire test apparatus. The telescopic stroke and speed of the drive assembly 1, as well as the required maximum and minimum displacements of the loading rod 3, were set according to the test requirements. The drive assembly 1 was activated and subjected to horizontal telescopic movement. As the drive assembly 1 extended and retracted, the triangular arm 2 rotated about its right-angle end 21, thereby moving the loading rod 3 vertically. The movement of the loading rod 3 stretched or compressed the air spring, simulating the vertical loading conditions encountered in actual operating conditions. During the loading process, a data acquisition system was used to record the displacement of the loading rod 3, the loading force, and the deformation of the air spring in real time for evaluating the durability of the air spring.

[0060] Depending on the test requirements, multiple cyclic loading tests can be performed to simulate the fatigue of the air spring during long-term use. A certain pause time can be set between each cyclic loading to allow the air spring to recover a certain elasticity and avoid overheating or excessive deformation caused by continuous loading.

[0061] This embodiment achieves efficient conversion from horizontal drive to vertical loading through the jib 2. Specifically, while the drive assembly 1 telescopes horizontally, the jib 2 can rotate around its right-angled end 21, thereby converting the horizontal force of the drive assembly 1 into vertical movement of the loading rod 3. This simplifies the loading path and improves energy conversion efficiency. Furthermore, by switching the loading direction, the jib 2 in this embodiment avoids the need for complex gantry or other support structures required in traditional vertical loading methods, significantly reducing space usage and manufacturing costs.

[0062] Due to the rotational nature of triangular arm 2, the vertical position of loading rod 3 can be flexibly adjusted according to loading requirements, enabling the test apparatus to easily accommodate diverse air spring testing requirements, including those of varying sizes, mounting heights, and loading ranges. Furthermore, by adjusting the extension and retraction of drive assembly 1, the vertical movement distance of loading rod 3 can be further precisely controlled, enabling even more refined loading control.

[0063] In this embodiment, a right-angle end 21 is formed on the triangular arm 2. The right-angled triangle structure has high structural stability, can effectively convert the horizontal driving force into the vertical loading force, and provide stable support through the right-angle side when bearing the load in the vertical direction.

[0064] In this embodiment, the drive assembly 1 is preferably a hydraulic cylinder, which has high-precision force and position control capabilities. By adjusting the pressure and flow of the hydraulic system, the hydraulic cylinder's extension and retraction speed and force can be precisely controlled, thereby achieving precise control of the vertical movement of the loading rod 3. The hydraulic cylinder can generate a large thrust and is suitable for test scenarios requiring large loads. In the vertical loading endurance test of passenger car air springs, the vertical vibration of the vehicle under different weights and speeds can be simulated to ensure that the loading force is fully transmitted to the air spring.

[0065] like Figure 1 and Figure 2 As shown, it also includes a first movable connection component 5, and the other end of the driving component 1 is movably connected to the first side 22 through the first movable connection component 5.

[0066] When the jib 2 rotates, the first side 22 moves along a circular arc. If a rigid connection were used, one end of the drive assembly 1 would be subjected to a large lateral force, potentially causing the connection to fail or be damaged. This embodiment utilizes the design of the first movable connection assembly 5, which allows a certain amount of movement or freedom between the drive assembly 1 and the first side 22 of the jib 2. This allows the drive assembly 1 to more smoothly drive the jib 2 to rotate during extension and retraction, reducing friction and resistance caused by the rigid connection and improving operational efficiency.

[0067] In this embodiment, the first movable connection component 5 is preferably a hinge component. Since the first side 22 inevitably drives one end of the driving component 1 to move up or down during the rotation of the triangular arm 2, the hinge component can ensure a stable and flexible connection between the driving component 1 and the triangular arm 2.

[0068] like Figure 1 、 Figure 2 and Figure 9 As shown, the first movable connection component 5 includes a first joint bearing 51 and a first articulated seat 52. The first joint bearing 51 is installed on the driving component 1, and the first articulated seat 52 is installed on the first side 22. The first joint bearing 51 and the first articulated seat 52 are hinged to each other so that the driving component 1 is hinged to the triangular arm 2.

[0069] The first joint bearing 51 is capable of multi-directional rotation and swing within a certain range, allowing the first joint bearing 51 to adapt well to the displacement and angular changes generated by the triangle arm 2 during rotation. The first articulated seat 52 is mounted on the first side 22 of the triangle arm 2, corresponding to the first joint bearing 51. The first joint bearing 51 and the first articulated seat 52 can be hingedly connected through spherical contact. When the drive assembly 1 performs telescopic movement, it transmits force to the first articulated seat 52 through the first joint bearing 51, thereby driving the triangle arm 2 to rotate around the right-angle end 21.

[0070] In this embodiment, Figure 9 As shown, the first joint bearing 51 includes a connecting column 511, an outer spherical end 512 and an inner spherical end 513. The inner spherical end 513 is located inside the outer spherical end 512, and the inner spherical end 513 can rotate universally inside the outer spherical end 512. When in use, the connecting column is used to tighten on the output end of the drive assembly 1, and the inner spherical end 513 is connected to the first hinge seat 52, thereby realizing the movable connection between the first side 22 and the drive assembly 1.

[0071] like Figure 3 and Figure 9 As shown, a first mounting hole 521 is formed on the first hinge seat 52, and a plurality of second mounting holes 221 are formed on the first side 22, and the second mounting holes 221 are evenly distributed along the length direction of the first side 22; the first mounting hole 521 is adapted to the second mounting holes 221 so that the first hinge seat 52 can be installed on the first side 22.

[0072] In this embodiment, the cooperation between the first mounting hole 521 formed on the first articulated seat 52 and the multiple second mounting holes 221 formed on the first side 22 is not only used to fix the position of the first articulated seat 52 on the triangular arm 2, but also to achieve different transmission ratios by selecting appropriate hole positions. Different positions of the second mounting holes 221 correspond to different lever arm lengths (i.e., the distance from the first articulated seat 52 to the rotation center point of the triangular arm 2). A longer lever arm can produce a larger input torque; a shorter lever arm may produce a smaller input torque. In this embodiment, by selecting appropriate hole positions, the lever arm length can be adjusted, thereby adjusting the swing amplitude and path of the triangular arm 2 during the rotation process to better simulate the vertical loading conditions in actual working conditions.

[0073] In this embodiment, Figure 3 As shown in the figure, the distances between the upper and lower articulated seats and the rotation center are 240mm and 480mm respectively. Therefore, the force ratio between the input and output ends is 2:1, and the speed ratio is 1:2. This allows the hydraulic servo system with a large load and low linear speed to output a small load and high linear speed.

[0074] like Figure 1 and Figure 2 As shown, it also includes a second movable connection component 6, and the other end of the loading rod 3 is movably connected to the second side 23 through the second movable connection component 6.

[0075] The second movable connection assembly 6 is similar to the first movable connection assembly 5. The second movable connection assembly 6 ensures the flexibility between the loading rod 3 and the triangular arm 2. The loading rod 3 can move or rotate to a certain extent relative to the triangular arm 2 during the vertical loading process to adapt to the deformation of the air spring during the loading process and reduce the stress concentration and damage risk caused by the rigid connection.

[0076] like Figure 1-Figure 3 As shown, the second movable connection component 6 includes a second joint bearing (not shown in the figure) and a second articulated seat 61. The second joint bearing is installed on the loading rod 3, and the second articulated seat 61 is installed on the second side 23. The second joint bearing is hinged to the second articulated seat 61 so that the loading rod 3 is hinged to the triangular arm 2.

[0077] The second spherical bearing is capable of accommodating various angle and displacement changes that may occur between the loading rod 3 and the yoke 2 during loading. A second articulated seat 61 is mounted on the second side 23 of the yoke 2, corresponding to the second spherical bearing. The second spherical bearing and the second articulated seat 61 are articulated via spherical contact. When the loading rod 3 is subjected to a vertical loading force, the force is transmitted to the second articulated seat 61 via the second spherical bearing, thereby driving the yoke 2 to rotate about the right-angle end 21.

[0078] like Figure 3As shown, a third mounting hole 611 is formed on the second hinge seat 61, and a plurality of fourth mounting holes 231 are formed on the second side 23, and the fourth mounting holes 231 are evenly distributed along the length direction of the second side 23; the third mounting hole 611 is adapted to the fourth mounting holes 231 so that the second hinge seat 61 can be installed on the second side 23.

[0079] In this embodiment, the third mounting hole 611 formed on the second hinge base and the plurality of fourth mounting holes 231 formed on the second side 23 not only secure the second hinge base on the yoke 2 but also enable different transmission ratios to be achieved by selecting appropriate hole positions. Different positions of the fourth mounting holes 231 correspond to different lever arm lengths (i.e., the distance from the second hinge base to the rotation center of the yoke 2).

[0080] like Figures 1-4 As shown, a rotating assembly 7 is further included. The right-angle end 21 of the triangular arm 2 is connected to the rotating assembly 7. The rotating assembly 7 is used to rotatably support the triangular arm 2 on the ground.

[0081] The rotating assembly 7 provides a stable support point for the triangular arm 2, ensuring that the triangular arm 2 can maintain a stable posture during the loading process and avoid shaking or tilting.

[0082] like Figure 4 As shown, the rotating assembly 7 includes a base 71, a bearing 72 and a rotating shaft 73. The base 71 is used to support the ground; the bearing 72 is mounted on the base 71, and the rotating shaft 73 is rotatably mounted on the bearing 72; a third mounting hole is formed on the right-angle end 21, and the third mounting hole is adapted to the rotating shaft 73. The rotating shaft 73 can pass through the third mounting hole to rotatably mount the triangular arm 2 on the bearing 72.

[0083] Base 71 is firmly supported on the ground, providing a stable foundation for jib 2. Bearing 72 is mounted on base 71, effectively reducing friction and wear, allowing shaft 73 to rotate smoothly with low resistance. The design of rotating assembly 7 ensures that jib 2 maintains a stable posture during loading, preventing shaking or tilting that could affect the accuracy of test results.

[0084] In this embodiment, Figure 4As shown, the base 71 includes an iron floor connecting plate 711, a mounting base 712, and a bearing seat 713. These three components are arranged in order from bottom to top, with the bearing 72 mounted on the bearing seat 713. The bearing 72 includes a bearing body 721, a bearing end cap 722, a bearing retainer 723, and a bearing retainer ring 724. During installation, the rotating shaft 73 is passed through the yoke 2, and the bearing retainer ring 724 is passed through the rotating shaft 73, connecting the three. The inner ring of the bearing body 721 is then mounted on both ends of the rotating shaft 73, while the outer ring is embedded in the bearing seat 713. The bearing end cap 722 is connected to the bearing seat 713 to restrict the movement of the outer ring of the rotating shaft 73. The bearing retainer 723 is connected to the rotating shaft 73 to restrict the movement of the inner ring of the rotating shaft 73. The lower end surface of the bearing seat 713 is connected to the mounting base 712, and two locating pins are installed to restrict radial movement of both.

[0085] like Figure 2 As shown, it also includes an insulation box 8 and an insulation box bracket 9, and the air spring is fixed in the insulation box 8; the insulation box 8 is arranged above the loading rod 3 through the insulation box bracket 9, and at least part of the loading rod 3 extends into the insulation box 8 to connect with the air spring (not shown in the figure).

[0086] The insulation box 8 is used to maintain the stability of the internal temperature. In the durability test of the air spring, temperature is an important influencing factor. The insulation box 8 can be used to simulate the working environment under different temperature conditions to evaluate the performance of the air spring at different temperatures. At the same time, the insulation box 8 can also effectively isolate the interference of the external environment on the test, such as temperature fluctuations, humidity changes, dust pollution, etc., which helps to reduce test errors and improve the accuracy of test results. The insulation box bracket is used to firmly support the insulation box above the loading rod 3, which not only ensures the stability of the insulation box 8, but also enables the loading rod 3 to be accurately connected to the air spring in the insulation box 8.

[0087] In this embodiment, the insulation box 8 is preferably made of polyurethane thermal insulation material, which effectively prevents heat transfer and maintains a stable internal temperature. In the passenger car air spring durability vertical loading test rig, the polyurethane insulation box ensures that the air spring maintains a stable temperature during testing, reducing the impact of the external environment on the test results. Furthermore, its excellent thermal insulation and waterproof and moisture-proof properties provide additional protection for the air spring, ensuring smooth testing and accurate results.

[0088] In this embodiment, Figure 1 and Figure 2 As shown, the passenger car air spring durability vertical loading test device also includes three columns 10 and a first pad 11. The three columns 10 are equidistantly supported on the ground, and the air suspension system (including the air spring) is located in an insulation box 8 (not shown in the figure). The insulation box 8 is composed of six panels, such as Figure 6 As shown, a plurality of sixth mounting holes 811 are provided on the back plate 81 , and the sixth mounting holes 811 are adapted to the first cushion blocks 11 . The back plate 81 can be vertically mounted on the three columns 10 through the first cushion blocks 11 .

[0089] In this embodiment, Figure 1 As shown, a suspension mounting base plate 12 is provided within the insulated box 8 and is vertically mounted on the back plate 81. The air suspension system is mounted on the suspension mounting base plate 11 via a suspension fixture. The suspension mounting base plate 11 is provided with a number of evenly distributed threaded holes to allow for flexible installation of various types of suspension fixtures.

[0090] like Figure 1 and Figure 2 As shown, multiple groups of air suspension systems (such as samples and accompanying test pieces) can be tested for durability in the insulation box 8 at the same time. Figure 7 As shown, the bottom plate 82 is provided with a plurality of through holes 821 for a plurality of loading rods 3 to extend therethrough.

[0091] like Figure 8 As shown, an observation window 831 is provided on the front plate 83 of the heat preservation box 8 so that the staff can observe the sample during the test.

[0092] like Figure 5 As shown, in this embodiment, preferably, the insulated box bracket 9 is a width-adjustable structure, and a second pad 92 is provided on the crossbeam 91 of the insulated box bracket 9. The width of the insulated box bracket 9 is adjusted by adjusting the insertion length of the second pad 92.

[0093] The serial numbers of the embodiments of this application are for descriptive purposes only and do not represent the superiority or inferiority of the embodiments. The above are only preferred embodiments of this application and do not limit the scope of the patent of this application. Any equivalent structure or equivalent process transformation made by using the contents of the description and drawings of this application, or directly or indirectly applied in other related technical fields, are also included in the scope of patent protection of this application.

Claims

1. A vertical endurance loading test device for passenger car air springs, characterized in that: include: A driving assembly (1), a triangular arm (2), a loading rod (3) and a mounting seat (4); the triangular arm (2) is formed with a right-angle end (21), a first side (22) and a second side (23); and the triangular arm (2) is configured to be rotatable with the right-angle end (21) as the center; One end of the driving component (1) is hinged on the mounting seat (4), and the other end of the driving component (1) is movably connected to the first side (22); the driving component (1) is configured to be capable of telescopic movement in the horizontal direction, and the driving component (1) can pull the first side (22) during the telescopic process to make the triangular arm (2) rotate around the right-angle end (21); One end of the loading rod (3) is used to connect to the air spring, and the other end of the loading rod (3) is movably connected to the second side (23). The loading rod (3) is arranged in a vertical direction, and the triangular arm (2) can drive the loading rod (3) to move in the vertical direction during rotation to stretch or squeeze the air spring.

2. A vertical endurance loading test device for passenger car air springs according to claim 1, characterized in that: It also includes a first movable connection component (5), and the other end of the driving component (1) is movably connected to the first side (22) through the first movable connection component (5).

3. A vertical endurance loading test device for passenger car air springs according to claim 2, characterized in that: The first movable connection component (5) includes a first joint bearing (51) and a first articulated seat (52), wherein the first joint bearing (51) is mounted on the driving component (1), and the first articulated seat (52) is mounted on the first side (22), and the first joint bearing (51) and the first articulated seat (52) are articulated to enable the driving component (1) to be articulated to the triangular arm (2).

4. A vertical endurance loading test device for passenger car air springs according to claim 3, characterized in that: A first mounting hole (521) is formed on the first hinge seat (52), and a plurality of second mounting holes (221) are formed on the first side edge (22), wherein the second mounting holes (221) are evenly distributed along the length direction of the first side edge (22); the first mounting hole (521) is adapted to the second mounting holes (221) so that the first hinge seat (52) can be mounted on the first side edge (22).

5. A vertical endurance loading test device for passenger car air springs according to any one of claims 1 to 3, characterized in that: It also includes a second movable connection component (6), and the other end of the loading rod (3) is movably connected to the second side (23) through the second movable connection component (6).

6. A vertical endurance loading test device for passenger car air springs according to claim 5, characterized in that: The second movable connection assembly (6) includes a second joint bearing and a second articulated seat (61), wherein the second joint bearing is mounted on the loading rod (3), and the second articulated seat (61) is mounted on the second side (23), and the second joint bearing and the second articulated seat (61) are articulated to enable the loading rod (3) to be articulated to the triangular arm (2).

7. A vertical endurance loading test device for passenger car air springs according to claim 6, characterized in that: A third mounting hole (611) is formed on the second hinge seat (61), and a plurality of fourth mounting holes (231) are formed on the second side edge (23), wherein the fourth mounting holes (231) are evenly distributed along the length direction of the second side edge (23); the third mounting hole (611) is adapted to the fourth mounting holes (231) so that the second hinge seat can be mounted on the second side edge (23).

8. The vertical endurance loading test device for passenger car air springs according to claim 1, characterized in that: It also includes a rotating assembly (7), the right-angle end (21) of the triangular arm (2) is connected to the rotating assembly (7), and the rotating assembly (7) is used to support the triangular arm (2) rotatably on the ground.

9. A vertical endurance loading test device for passenger car air springs according to claim 8, characterized in that: The rotating assembly (7) comprises a base (71), a bearing (72) and a rotating shaft (73), wherein the base (71) is used for supporting on the ground; the bearing (72) is mounted on the base (71), and the rotating shaft (73) is rotatably mounted on the bearing (72); a fifth mounting hole is formed on the right-angle end (21), the fifth mounting hole is adapted to the rotating shaft (73), and the rotating shaft (73) can pass through the fifth mounting hole to rotatably mount the triangular arm (2) on the bearing (72).

10. A vertical endurance loading test device for passenger car air springs according to claim 1, characterized in that: It also includes an insulation box (8) and an insulation box bracket (9), and the air spring is fixed in the insulation box (8); the insulation box (8) is arranged above the loading rod (3) through the insulation box bracket (9), and at least a portion of the loading rod (3) extends into the insulation box (8) to be connected to the air spring.

Images