Test device and test system

Abstract

The application relates to the technical field of brake testing equipment, and provides a testing device and a testing system, the testing device comprising a base body, a driving part arranged on the base body, a swing arm assembly hingedly connected to the base body, and a transmission part arranged between the driving part and the swing arm assembly. A mounting part for mounting a brake master cylinder assembly is arranged on the base body, the driving part can drive the swing arm assembly to swing through the transmission part, and the swing arm assembly can push the piston to move along the axial direction of the swing arm assembly. The testing device can better simulate the actual working state of a drum brake master cylinder assembly in driving braking. The swing of the swing arm assembly can simulate the dynamic load generated due to road bumping and braking action in the vehicle driving process, and can effectively avoid the problem that the dynamic sealing defect cannot be obtained through the traditional static test. Therefore, the testing device can effectively verify the reliability of the piston sealing property under the dynamic working condition, and can have a more accurate testing effect.

Description

Technical Field

[0001] This application relates to the field of brake technology, and in particular to a testing device and testing system. Background Technology

[0002] The current testing field for drum brake caliper assemblies faces equipment challenges. Basic testing devices are limited in function and cannot effectively verify the potential failure modes of the caliper assembly under dynamic loads, resulting in test results that fail to accurately reflect the actual operational reliability of the caliper assembly. In particular, the accuracy of piston sealing tests is poor. When the piston seal is poor, insufficient piston thrust cannot be generated, directly leading to brake failure and seriously endangering driving safety. Utility Model Content

[0003] In view of this, the present application aims to provide a testing device to improve the accuracy of piston sealing tests.

[0004] To achieve the above objectives, the technical solution of this application is implemented as follows: A testing apparatus suitable for testing the piston sealing performance of a brake caliper assembly includes a base, a drive unit disposed on the base, a swing arm assembly hinged to the base, and a transmission unit disposed between the drive unit and the swing arm assembly. The base is provided with a mounting part for mounting the brake cylinder assembly. The drive part can drive the swing arm assembly to swing through the transmission part and cause the swing arm assembly to push the piston to move along its own axis.

[0005] Furthermore, the swing arm assembly includes two swing arms spaced apart to form a receiving space, and a connecting arm hinged between one end of the two swing arms. The other ends of both swing arms are hinged to the base, and the brake caliper assembly mounted through the mounting part extends into the receiving space so that the pistons on both sides are pushed by the corresponding swing arms.

[0006] Furthermore, each of the aforementioned swing arms includes a swing arm body and a push rod disposed on the swing arm body; The push rod protrudes into the receiving space and can be inserted into the piston, thus restricting the piston from rotating about its own axis.

[0007] Furthermore, the push rod is screwed onto the swing arm body; The piston has a groove at its end, and the push rod can be inserted into the groove. The push rod has a limiting surface that abuts against the side wall of the groove to restrict the piston from rotating around its own axis.

[0008] Furthermore, the swing arm body is provided with a sleeve, the push rod is screwed into the sleeve, and a nut is screwed onto the push rod, the nut abutting against the sleeve.

[0009] Furthermore, the sleeve is screwed onto the swing arm body, and a limiting member is provided on the swing arm body; The limiting member is used to restrict the rotation of the sleeve relative to the swing arm body.

[0010] Furthermore, the transmission unit includes an eccentric wheel disposed on the drive shaft of the drive unit; The drive unit is used to output rotational power, and the eccentric wheel rotates with the drive shaft to push each of the swing arms to swing.

[0011] Furthermore, the transmission unit includes a bearing sleeved on the eccentric wheel, the bearing being located within the receiving space and abutting against the swing arms on both sides; The eccentric wheel pushes each of the swing arms to swing through the bearing.

[0012] Furthermore, each of the swing arm bodies is provided with a protruding portion that extends into the receiving space; The bearing abuts against the protruding portions of the two swing arm bodies.

[0013] Compared with related technologies, this application has the following advantages: (1) The test device described in this application, by setting a base for mounting the brake caliper, a swing arm assembly hinged to the base, and enabling the drive unit to drive the swing arm assembly to swing and push the piston to move axially through the transmission unit, can better simulate the actual working state of the drum brake caliper assembly in service braking, and can effectively avoid the problem that traditional static testing cannot obtain dynamic sealing defects.

[0014] Furthermore, the axial pushing of the piston by the swing arm assembly can test the piston's sealing performance when it moves under force, effectively detecting whether leakage causes insufficient thrust or movement stagnation. Therefore, this testing device can effectively verify the reliability of the piston's sealing performance under dynamic operating conditions and provide relatively accurate test results. Moreover, this testing device has a simple structure and low cost.

[0015] (2) By setting two swing arms arranged at intervals, they can act synchronously on the pistons on both sides, so that the movement state of the piston is more consistent with the actual braking process. This is a test method that is more in line with the actual working conditions, which can further improve the authenticity and accuracy of piston sealing verification and ensure that the test results can directly reflect the actual working reliability of the pump assembly.

[0016] (3) By setting a push rod that can be inserted into the piston to restrict the piston rotation, the piston can be constrained to move only along its own axis, which can better match the actual braking trajectory, thereby further improving the accuracy of the sealing performance test of the seal.

[0017] (4) By screwing the push rod onto the rocker arm body, its protrusion length into the receiving space can be adjusted by rotating the push rod. This allows for flexible adjustment of the push rod's insertion depth to accommodate the groove depth of pistons in different specifications of pump assemblies, improving the versatility of the device. Simultaneously, the larger force-bearing area of ​​the limiting surface allows it to withstand greater rotational resistance, effectively ensuring that the piston does not rotate circumferentially and guaranteeing the accuracy of the sealing test data. Furthermore, the limiting surface structure is simple and easy to design and implement.

[0018] (5) By setting a sleeve on the swing arm body, the sleeve can be made of high-strength metal material, and its internal thread can be designed to have a longer mating length to improve the mating strength with the push rod thread, thereby extending the overall service life of the swing arm assembly. In addition, the friction between the nut and the sleeve can be used to lock the position of the push rod, preventing the thread from rotating relative to the other due to vibration. This ensures that the push rod always maintains the preset protrusion length and insertion depth, which helps to further improve the accuracy of piston sealing tests.

[0019] (6) By screwing the sleeve onto the swing arm body and setting a limiting component to restrict the rotation of the sleeve, when the internal thread of the sleeve is worn or a different specification sleeve needs to be replaced (such as a push rod that is compatible with different thread specifications), the limiting component can be removed and the old sleeve can be unscrewed to replace the new part. There is no need to modify the swing arm body, which can save modification time.

[0020] (7) By including the eccentric wheel on the drive shaft in the transmission part, the structure is simple. Moreover, by designing an eccentric wheel with a specific eccentricity, the movement stroke of the piston in actual braking can be better matched, so that the swing arm swing amplitude is more consistent with the actual working range of the piston, which is conducive to further improving the simulation effect of dynamic test on actual working conditions.

[0021] (8) By setting bearings, sliding friction can be converted into rolling friction, which can significantly reduce the wear of the contact part between the eccentric wheel and the swing arm, so that the component can maintain stable structural dimensions during long-term durability testing, effectively avoid the deviation of swing amplitude caused by wear, and extend the life of the testing device.

[0022] (9) By setting a protruding part that protrudes into the accommodating space, the width of the accommodating space layout area can be reduced, thereby allowing the use of smaller bearings and reducing processing costs. Moreover, the setting of the protruding part can increase the structural strength of this part of the swing arm body, effectively reducing the risk of deformation caused by local stress concentration of the swing arm, and helping to extend the service life of the swing arm assembly.

[0023] Another object of this application is to provide a test system, including the test apparatus as described above, and a hydraulic device for connecting to the brake caliper assembly.

[0024] The testing system described in this application can effectively simulate the actual working state of the drum brake caliper assembly during vehicle braking, effectively verify the reliability of piston sealing under dynamic conditions, and provide accurate testing results. Attached Figure Description

[0025] The accompanying drawings, which form part of this application, are used to provide a further understanding of this application. The illustrative embodiments and descriptions of this application are used to explain this application and do not constitute an undue limitation of this application. In the drawings: Figure 1 This is a schematic diagram of the test device described in the embodiments of this application; Figure 2 This is a schematic diagram of the test device described in an embodiment of this application from another perspective; Figure 3 This is a schematic diagram of the test device described in an embodiment of this application from another perspective; Figure 4 for Figure 3 Side sectional view along line AA; Figure 5 for Figure 4 Enlarged view of section B; Figure 6 This is a partial structural schematic diagram of the brake caliper assembly described in an embodiment of this application; Figure 7 This is a schematic diagram of the piston body described in an embodiment of this application; Figure 8 This is a schematic diagram of the test apparatus described in the embodiments of this application when the substrate and cover are removed; Figure 9 for Figure 8 A schematic diagram of the structure shown from another perspective; Figure 10 This is a partial structural schematic diagram of the testing device described in the embodiments of this application; Figure 11 This is an assembly diagram of the swing arm assembly and mounting block described in the embodiments of this application; Figure 12This is a schematic diagram of the swing arm structure described in the embodiments of this application; Figure 13 This is a schematic diagram of the swing arm described in an embodiment of this application from another perspective; Figure 14 for Figure 13 A cross-sectional view of the CC line; Figure 15 This is a schematic diagram of the eccentric wheel described in an embodiment of this application.

[0026] Explanation of reference numerals in the attached figures: 1. Base; 2. Servo motor; 3. Cover; 4. Swing arm assembly; 5. Brake slave cylinder assembly; 6. Second bearing; 7. Eccentric wheel; 8. Flat key; 9. Set screw; 10. Retaining ring; 11. Connecting seat; 12. Coupling; 101. Substrate; 102. Mounting plate; 103. Mounting block; 104. Mounting bracket; 1041. Base plate; 1042. Main board; 10421. Mounting hole; 1043. Baffle; 201, Drive shaft; 2011, First shaft body; 2012, Second shaft body; 401, swing arm; 4011, protruding part; 402, connecting arm; 403, sleeve; 404, push rod; 4041, limiting surface; 405, limiting component; 501. Piston body; 5011. Groove; 502. Piston screw; 503. Seal; 504. Transmission gear; 701, Part 1; 702, Part 2; 703, Shoulder; 704, Clearance Groove. Detailed Implementation

[0027] To make the technical solution and advantages of this application clearer, the following detailed description is provided in conjunction with the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative and not intended to limit the scope of this application.

[0028] It should be noted that, unless otherwise specified, the embodiments and features described in this application can be combined with each other.

[0029] Furthermore, it should be noted that in the description of this application, if terms such as "upper," "lower," "inner," or "outer" appear, indicating orientation or positional relationship, these are based on the orientation or positional relationship shown in the accompanying drawings and are only for the convenience of describing this application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation on this application. In addition, if terms such as "first" or "second" appear, they are also used for descriptive purposes only and should not be construed as indicating or implying relative importance.

[0030] Furthermore, in the description of this application, unless otherwise expressly defined, the terms "installation," "connection," "joining," and "connector" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal connection between two components. Those skilled in the art can understand the specific meaning of the above terms in this application in light of the specific circumstances.

[0031] In this application, the terms "one embodiment," "some embodiments," "example," "specific example," or "some examples," etc., refer to a specific feature, structure, material, or characteristic described in connection with that embodiment or example, which is included in at least one embodiment or example of this application. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples.

[0032] The present application will now be described in detail through exemplary embodiments. However, it should be understood that, without further description, elements, structures, and features in one embodiment may be advantageously incorporated into other embodiments.

[0033] An embodiment of the first aspect of this application provides a testing apparatus suitable for testing the piston sealing performance of a brake caliper assembly 5, particularly suitable for a drum brake caliper assembly 5.

[0034] In related technologies, the drum brake caliper assembly 5 is a core actuator. During vehicle braking, the brake hydraulic pressure generated by the master cylinder is transmitted to the caliper assembly through the brake lines, driving the piston to move and achieve the braking function. Therefore, the caliper assembly's ability to withstand dynamic loads, its sealing performance, and its durability are crucial. If the caliper assembly fails and causes abnormal braking, it will pose a serious threat to driving safety. Therefore, targeted testing of the caliper assembly has become a necessary step in the production and research and development of drum brake calipers.

[0035] However, the current testing field for drum brake caliper assemblies faces significant technical and equipment challenges. On the one hand, while high-end testing equipment offers relatively comprehensive functionality, its complexity and high procurement and maintenance costs place a heavy economic burden on small and medium-sized enterprises that only need to conduct simple oscillation tests to verify basic dynamic performance. On the other hand, existing basic testing equipment has limited functionality and cannot effectively verify the potential failure modes of the caliper assembly under dynamic loads, resulting in test results that fail to accurately reflect the actual operational reliability of the caliper assembly.

[0036] From the perspective of the performance requirements of the brake caliper assembly itself, its operational stability is constrained by multiple key factors. In particular, when the piston seal is poor, sufficient piston thrust cannot be generated, directly leading to brake failure and seriously endangering driving safety. Furthermore, regarding the testing loading system, the three mainstream methods currently available—mechanical loading, pneumatic loading, and hydraulic loading—all have significant limitations and are difficult to match the testing requirements of the drum brake caliper assembly. Pneumatic loading cannot achieve stable loading at the required frequency, making it difficult to meet dynamic testing requirements. While hydraulic loading can provide adjustable pressure and a larger loading force, the overall equipment cost is high, and subsequent maintenance is cumbersome.

[0037] In view of this, in order to overcome the shortcomings of related technologies, the testing device in this embodiment combines... Figures 1 to 5 As shown, the overall design includes a base 1, a drive unit mounted on the base 1, a swing arm assembly 4 hinged to the base 1, and a transmission unit located between the drive unit and the swing arm assembly 4. The base 1 has a mounting portion for mounting the brake caliper assembly 5. The drive unit can drive the swing arm assembly 4 to swing via the transmission unit, causing the swing arm assembly 4 to push the piston along its own axial direction.

[0038] Therefore, by setting up a base 1 for mounting the brake caliper, and a swing arm assembly 4 hinged to the base 1, and enabling the drive unit to drive the swing arm assembly 4 to swing and push the piston to move axially via the transmission unit, the actual working state of the drum brake caliper assembly 5 during vehicle braking can be simulated well. The swinging of the swing arm assembly 4 can simulate the dynamic load generated by road bumps and braking during vehicle operation, effectively avoiding the problem that traditional static testing cannot obtain dynamic sealing defects.

[0039] Furthermore, the axial pushing of the piston by the swing arm assembly 4 can reproduce the process of the piston being driven by the brake hydraulic pressure, allowing for the testing of the piston's sealing performance under load. This effectively detects whether leakage causes insufficient thrust or movement stagnation. Therefore, this testing device can effectively verify the reliability of the piston's sealing performance under dynamic operating conditions and provides relatively accurate test results. Moreover, this testing device has a simple structure and low cost.

[0040] Based on the above overview, to facilitate understanding of this embodiment, the structure of the brake caliper assembly 5 will be briefly described first. Specifically, the structure of the brake caliper assembly 5 mentioned in this embodiment is the same as that of the prior art, and refers to... Figure 6 and Figure 7 As shown, it has two pistons arranged opposite to each other. Each piston includes a piston screw 502 that rotates coaxially with the transmission gear 504, a piston body 501 screwed onto the piston screw 502, and a sealing element 503 (also referred to as a "seal cup" in related art) sleeved on the piston body 501.

[0041] The seal 503 is used to achieve a seal between the piston and the housing of the brake caliper assembly. The test device in this embodiment is mainly used to test the sealing performance of the seal 503. Furthermore, the other structures of the seal 503 and the brake caliper assembly 5 can be referred to in related technologies and will not be described in detail here.

[0042] As a specific embodiment, the base 1 of this embodiment includes a substrate 101, a mounting plate 102 disposed on the substrate 101, and a mounting block 103 and a mounting frame 104 disposed at a distance from the mounting plate 102. Specifically, the driving unit is a servo motor 2 disposed on the mounting plate 102, the swing arm assembly 4 is disposed on the mounting block 103, and the mounting part is disposed on the mounting frame 104.

[0043] Specifically, such as Figure 2 As shown, the mounting bracket 104 in this example includes a base plate 1041 connected to the substrate 101, a main plate 1042 disposed on the top of the base plate 1041, and baffles 1043 disposed on two opposite sides of the main plate 1042. Furthermore, a shaft hole is provided in the middle of the main plate 1042 for the drive shaft 201 of the drive unit to pass through. Specifically, the drive shaft 201 is rotatably disposed in this shaft hole via a first bearing, and the first bearing can be disposed on the main plate 1042 in any manner. Additionally, the top of the main plate 1042 is constructed in an L-shape to form a clearance space for the brake slave cylinder assembly 5.

[0044] The mounting section in this embodiment specifically includes three mounting holes 10421 located on the top of the main board 1042. Therefore, in actual use, the brake caliper assembly 5 can pass through the clearance space into the following receiving space and be fixed to the mounting bracket 104 through the three mounting holes. It should be noted that the structure of the base 1 is not limited to that shown in the figure; it is acceptable as long as it can accommodate the installation of the drive unit, the swing arm assembly 4, and the brake caliper assembly.

[0045] Continue to combine Figures 1 to 3 As shown, in some exemplary embodiments, the swing arm assembly 4 includes two swing arms 401 spaced apart to form a receiving space, and a connecting arm 402 hinged between one end of the two swing arms 401. The other end of each of the two swing arms 401 is hinged to the base 1, and the brake slave cylinder assembly 5, mounted via a mounting part, extends into the receiving space so that the pistons on both sides are pushed by the corresponding swing arms 401.

[0046] Because the pistons on both sides of the brake caliper assembly 5 are simultaneously subjected to hydraulic thrust, pushing the brake shoes on both sides to contact the brake drum, two spaced-apart swing arms 401 are used to correspond to the pistons on both sides of the caliper assembly. These swing arms act synchronously on the pistons, making their movement more consistent with the actual braking process. This provides a more realistic testing method that more accurately exposes sealing defects in the caliper assembly under real-world operating conditions. Therefore, the authenticity and accuracy of piston sealing verification are further improved, ensuring that the test results directly reflect the actual operational reliability of the caliper assembly.

[0047] In specific implementation, combined with Figures 8 to 11 As shown, the two swing arms 401, the connecting arm 402, and the base 1 form a parallelogram linkage structure. With this configuration, when the drive unit moves the connecting arm 402, the two swing arms 401, as a pair of opposite sides of the parallelogram, will swing synchronously with the mounting block 103 (hinge point) as the reference. This ensures that the pushing direction of the two swing arms 401 against the piston is always aligned with the piston axis, which can better avoid test errors caused by pushing angle deviation.

[0048] Among them, such as Figure 11 As shown, the mounting block 103 in this embodiment is elongated, with hinge holes at both ends that are respectively hinged to the two swing arms 401, and three fixing holes spaced apart in the middle. The mounting block 103 is fixed to the base plate 101 by bolts passing through the three fixing holes. In this example, to reduce processing costs, the structure of the connecting arm 402 is the same as that of the mounting block 103, and will not be described again here.

[0049] It should be noted that the structure of the mounting block 103 and the connecting arm 402 is not limited to that shown in the figure. Their structures can also be different, as long as they can achieve hinge connection with the two swing arms 401 respectively.

[0050] In some exemplary embodiments, each rocker arm 401 includes a rocker arm body and a push rod 404 disposed on the rocker arm body. The push rod 404 protrudes into the receiving space and can be inserted into the piston, restricting the piston's rotation about its own axis. By providing a push rod 404 that can be inserted into the piston to restrict its rotation, the piston can be constrained to move only along its own axis, which better matches the actual braking trajectory, thereby further improving the accuracy of testing the sealing performance of the seal 503.

[0051] Furthermore, by using the push rod 404 to push the piston, compared to the rocker arm 401 pushing the piston via a flat surface, it is easier to effectively ensure that the pushing force is transmitted along the piston axis, thus guaranteeing the stability of power transmission. This protects the piston and sealing ring from damage by non-axial forces while ensuring the accurate transmission of the test load, avoiding fluctuations in test data caused by unstable force transmission.

[0052] In specific implementation, such as Figure 12 As shown, the swing arm body is generally elongated, with connecting ears at its upper and lower ends respectively, which are hinged to the mounting block 103 and the connecting arm 402, and each connecting ear has a connecting hole. The connecting ears at both ends can be inserted into the mounting block 103 and the connecting arm 402 respectively, and are hinged together with the connecting arm 402 and the mounting block 103 through a connecting shaft.

[0053] It is understandable that, in addition to making the rocker arm 401 include the rocker arm body and the push rod 404 provided on the rocker arm body, the rocker arm 401 can also include only the rocker arm body, as long as the rocker arm body can push the piston.

[0054] In some exemplary embodiments, the push rod 404 is screwed onto the rocker arm body. Furthermore, the piston end has a groove 5011 into which the push rod 404 can be inserted. The push rod 404 has a limiting surface 4041 that abuts against the side wall of the groove 5011 to restrict the piston from rotating about its own axis.

[0055] At this point, by screwing the push rod 404 onto the swing arm body, its protrusion length into the receiving space can be adjusted by rotating the push rod 404. This allows for flexible adjustment of the insertion depth of the push rod 404 to accommodate the groove depth of pistons in different specifications of brake assemblies, ensuring full contact between the limiting surface and the groove sidewall, thus improving the versatility of this testing device. Simultaneously, the protrusion length of the push rod 404 can be fine-tuned according to the actual piston stroke, allowing the push stroke to better match the piston movement range during brake braking, improving the fit between the test and actual working conditions. Furthermore, it facilitates the disassembly and replacement of the push rod 404.

[0056] By providing a limiting surface 4041 on the push rod 404 that abuts against the side wall of the groove 5011, the rotation of the groove 5011 is restricted. The larger force-bearing area of ​​the limiting surface 4041 allows it to withstand greater rotational resistance, effectively ensuring that the piston does not rotate circumferentially and guaranteeing the accuracy of the sealing test data. Furthermore, the limiting surface 4041 has a simple structure, facilitating design and implementation.

[0057] In some exemplary embodiments, the swing arm body is provided with a sleeve 403, a push rod 404 is screwed into the sleeve 403, and a nut is screwed onto the push rod 404, the nut abutting against the sleeve 403. With this configuration, the sleeve 403 can be made of a high-strength metal material, and its internal threads can be designed to have a longer mating length to improve the mating strength with the threads of the push rod 404.

[0058] This structure avoids damage caused by the direct force of the thread on the swing arm body and extends the overall service life of the swing arm assembly 4. Even if the thread of the sleeve 403 wears, only the sleeve 403 needs to be replaced, without scrapping the swing arm 401, further reducing maintenance costs. In addition, after adjusting the axial length of the push rod 404, tightening the nut to make it tightly abut against the end face of the sleeve 403 can lock the position of the push rod 404 using the friction between the nut and the sleeve 403, preventing relative rotation of the thread due to vibration.

[0059] Therefore, the pre-set protrusion length and insertion depth of the push rod 404 can always be maintained, which can effectively prevent the push rod 404 from shifting position due to external force or vibration, and help to further improve the accuracy of piston sealing test.

[0060] Combination Figures 12 to 14 As shown, in a specific implementation, the push rod 404 can be directly adopted from the existing screw, and both ends of the sleeve 403 are respectively protruding outwards towards both ends of the swing arm body. This allows for a longer mating length between the sleeve 403 and the push rod 404, ensuring better stability of the push rod 404 and effectively preventing it from loosening.

[0061] It is understandable that, in addition to setting a sleeve 403 on the swing arm body and screwing the push rod 404 into the sleeve 403, it is also feasible to directly set a threaded hole on the swing arm body and directly connect the push rod 404 into the threaded hole.

[0062] In some exemplary embodiments, the sleeve 403 is screwed onto the rocker arm body, and a limiting member 405 is provided on the rocker arm body to limit the rotation of the sleeve 403 relative to the rocker arm body. By screwing the sleeve 403 onto the rocker arm body and providing the limiting member 405 to limit the rotation of the sleeve 403, when the internal threads of the sleeve 403 are worn, or when it is necessary to replace the sleeve 403 with a different specification (such as a push rod 404 adapted to a different thread specification), it is only necessary to remove the limiting member 405 and unscrew the old sleeve 403 to replace the new part, without modifying the rocker arm body.

[0063] Compared to fixing the sleeve 403 to the swing arm body, this significantly reduces maintenance costs and downtime, and only the sleeve 403 needs to be replaced, without scrapping the entire swing arm assembly 4. If an upgrade to accommodate a large-diameter push rod 404 is required, the sleeve 403 with the corresponding internal thread specification can be directly replaced, without redesigning the structure of the swing arm 401.

[0064] It is understandable that, in addition to screwing the sleeve 403 onto the swing arm body, it is also feasible to directly weld or press-fit the sleeve 403 onto the swing arm body.

[0065] Continue to combine Figures 12 to 14 As shown, the sleeve 403 in this embodiment is specifically cylindrical, with a hexagonal operating portion at one end. This operating portion is adaptable to external operating tools, thereby facilitating the assembly and disassembly of the sleeve 403 onto the swing arm body, further improving the replacement efficiency of the sleeve 403. The limiting member 405 is specifically a set screw screwed onto the swing arm body, which abuts against the outer circumferential surface of the sleeve 403 to restrict its rotation. At this time, to prevent the set screw from loosening, a nut that abuts against the swing arm body is also screwed onto it.

[0066] In some exemplary embodiments, the transmission unit includes an eccentric wheel 7 mounted on the drive shaft 201 of the drive unit, and the drive unit outputs rotational power. The eccentric wheel 7 rotates with the drive shaft 201 and pushes each swing arm 401 to swing. By including the eccentric wheel 7 on the drive shaft 201 in the transmission unit, the structure is simple. Moreover, by designing the eccentric wheel 7 with a specific eccentricity, the movement stroke of the brake cylinder piston during actual braking can be better matched, making the swing amplitude of the swing arm 401 more consistent with the actual working range of the piston, which is beneficial to further improve the simulation effect of dynamic testing on actual working conditions.

[0067] Furthermore, compared to other transmission methods, when the drive shaft 201 rotates, the eccentric wheel 7 can directly contact the swing arm 401 and apply a pushing force, effectively avoiding power lag. Moreover, compared to hydraulic loading which requires an oil pump, pipelines, valve groups, etc., the eccentric wheel 7 transmission only requires two main components: the drive shaft 201 and the eccentric wheel 7. This greatly simplifies the transmission system structure, reduces equipment manufacturing costs, and is particularly suitable for the low-cost testing equipment needs of small and medium-sized enterprises.

[0068] In specific implementation, refer to Figure 8 and Figure 9As shown, the drive unit uses a servo motor 2, and its drive shaft 201 includes a first shaft 2011 connected to the rotor of the servo motor 2, and a second shaft 2012 connected to the first shaft 2011 via a coupling 12. In this embodiment, the eccentric wheel 7 is specifically fitted onto the second shaft 2012. In addition, in order to realize the mounting of the servo motor 2 on the mounting plate 102, a connecting seat 11 protruding outward to one side is provided on the housing of the servo motor 2. The second shaft 2012 of the drive shaft 201 is rotatably disposed in the connecting seat 11, and the connecting seat 11 is bolted to the mounting plate 102, thereby realizing the fixation of the servo motor 2 on the machine body.

[0069] In addition, such as Figure 1 As shown, to improve the overall aesthetics of this testing device, a cover 3 is provided on top of the connecting seat 11, and this cover 3 is connected to the mounting plate 102. In this embodiment, to achieve the connection between the eccentric wheel 7 and the second shaft 2012, combined with... Figure 5 and Figure 15 As shown, a keyway is provided on the outer circumferential surface of the second shaft 2012, and a flat key 8 is provided within the keyway. A clearance groove 704 is provided in the middle of the eccentric wheel 7 to avoid the flat key 8. Furthermore, a fastening hole communicating with the clearance groove 704 is provided on the eccentric wheel 7, and a fastening screw is provided within the fastening hole and connected to the flat key 8. Thus, the eccentric wheel 7 can be fastened to the second shaft 2012, thereby enabling synchronous rotation of the eccentric wheel 7 and the drive shaft 201.

[0070] It should be noted that, in addition to connecting the eccentric wheel 7 to the second shaft 2012 via the flat key 8, the eccentric wheel 7 can also be directly welded to the second shaft 2012 or connected together using other conventional methods.

[0071] In some exemplary embodiments, the transmission unit includes a bearing sleeved on the eccentric wheel 7. The bearing is located within a receiving space and abuts against the two side swing arms 401. The eccentric wheel 7 pushes each swing arm 401 to swing through the bearing. When the eccentric wheel 7 directly abuts against the swing arm 401, the relative motion between the two is sliding friction. The contact area between the swing arm 401 and the eccentric wheel 7 will experience severe wear due to continuous sliding. This not only shortens the service life of the eccentric wheel 7 and the swing arm 401, but also increases the pushing clearance due to wear, affecting the transmission effect.

[0072] At this point, by setting up a bearing, sliding friction can be converted into rolling friction. The inner ring of the bearing is fixed to the eccentric wheel 7 and rotates synchronously with the eccentric wheel 7, while the outer ring abuts against the swing arm 401, achieving relative motion through rolling. The coefficient of friction for rolling friction is much lower than that for sliding friction, thus significantly reducing the wear at the contact point between the eccentric wheel 7 and the swing arm 401. This allows the component to maintain stable structural dimensions during long-term durability testing, effectively avoiding deviations in the swing amplitude caused by wear, and extending the lifespan of the testing device.

[0073] In this embodiment, as Figure 15 As shown, the eccentric wheel 7 includes a first part 701 and a second part 702, with the outer diameter of the first part 701 being smaller than that of the second part 702. A shoulder 703 is provided at the end of the second part 702 away from the first part 701. The bearing in this embodiment is specifically connected to the second part 702, and for ease of distinction from the above, this bearing is referred to as the "second bearing 6". To achieve axial positioning of the second bearing 6, a retaining ring 10, secured with a set screw 9, is provided on the first part 701 of the eccentric wheel 7. The second bearing 6 is clamped between the retaining ring 10 and the shoulder 703. The retaining ring 10 can employ a conventional structure.

[0074] It should be noted that, in addition to using a retaining ring 10 to restrict the axial movement of one side of the second bearing 6, a slot can also be provided on the first part 701, and a retaining spring can be provided in the slot to restrict the axial displacement of the second bearing 6.

[0075] In some exemplary embodiments, each control arm body has a protruding portion 4011 extending into the receiving space, and the bearing abuts against the protruding portions 4011 of both control arm bodies. Since the receiving space needs to accommodate both the brake caliper assembly 5 and the bearing, and the brake caliper assembly 5 has a large width, if the bearing directly abuts against the plane of the control arm body, a larger bearing size would be required, which would increase manufacturing costs and weight.

[0076] Here, by providing a protruding portion 4011 that extends into the accommodating space, the width of the accommodating space layout area can be reduced, thereby allowing the use of smaller bearings and reducing manufacturing costs. Furthermore, the protruding portion 4011 increases the structural strength of this part of the swing arm body, effectively reducing the risk of deformation of the swing arm 401 due to localized stress concentration, and thus extending the service life of the swing arm assembly 4.

[0077] Combination Figure 10 and Figure 12As shown, in this embodiment, the protruding portion 4011 is located on the side of the swing arm body away from the connecting arm 402, and the protruding portion 4011 is an elongated strip extending along the length direction of the swing arm body. This structure allows the protruding portion 4011 to effectively strengthen the structural strength of the area, while also providing a large contact area with the second bearing 6, thereby ensuring that the swing arm 401 remains in contact with the second bearing 6 throughout its swinging motion.

[0078] It should be noted that, in actual implementation, the protruding part 4011 may not be set according to design requirements.

[0079] It is worth noting that, regarding the testing device in this embodiment, based on the above exemplary implementations, in specific implementation, as a preferred embodiment, it is still composed of... Figures 1 to 15 As shown, it may include, for example, a base 1, a drive unit provided on the base 1, a swing arm assembly 4 hinged to the base 1, and a transmission unit provided between the drive unit and the swing arm assembly 4.

[0080] The base 1 is provided with mounting holes for mounting the brake caliper assembly 5. The drive unit can drive the swing arm assembly 4 to swing through the transmission unit and make the swing arm assembly 4 push the piston to move along its own axis.

[0081] The rocker arm assembly 4 includes two rocker arms 401 spaced apart to form a receiving space, and a connecting arm 402 hinged between one end of the two rocker arms 401. Each rocker arm 401 includes a rocker arm body and a push rod 404 screwed onto the rocker arm body. The push rod 404 protrudes into the receiving space and can be inserted into the piston, restricting the piston from rotating around its own axis.

[0082] In the preferred embodiment of the above testing device, the specific settings and arrangements of the base 1, the swing arm assembly 4, etc. can still be referred to the descriptions in the above exemplary embodiments. Furthermore, in this preferred embodiment, the beneficial effects brought about by the design of the base 1, the swing arm assembly 4, etc. can also be referred to the descriptions in the above exemplary embodiments.

[0083] The testing device in this embodiment, with the design described above, can effectively simulate the actual working state of the drum brake caliper assembly 5 during vehicle braking, thus avoiding the problem that traditional static tests cannot capture dynamic sealing defects. Therefore, this testing device can effectively verify the reliability of piston sealing under dynamic conditions and provides accurate test results. Furthermore, this testing device has a simple structure and low cost.

[0084] An embodiment of the second aspect of this application provides a testing system, including the testing apparatus as claimed above, and a hydraulic device for connection to the brake caliper assembly 5.

[0085] The hydraulic system provides hydraulic pressure to the brake caliper assembly 5. This system typically includes a hydraulic power source module, a pressure regulation and control module, and an oil delivery and filtration module. Existing hydraulic systems can be used, and will not be described in detail here.

[0086] In this embodiment, before testing, the operator presets key parameters in the main control system, including the swing frequency (controlled by the speed of servo motor 2), the total number of cycles, and the applied hydraulic pressure. Then, the servo motor 2 is calibrated to ensure that the hydraulic device can be activated when the swing arm assembly 4 swings to its maximum angle, and that hydraulic unloading is completed after a preset time (e.g., 10ms).

[0087] After the test is started, the PLC control system (used for signal interaction with the main control system, the control system of servo motor 2, and the hydraulic device) synchronously sends the set parameters of the main control system to the control system of the servo motor and the hydraulic device. The servo motor 2 executes rotational motion according to the command, transmitting the rotational inertia to the eccentric wheel 7 through the drive shaft 201, and using the eccentric motion to drive the swing arm assembly 4 to swing left and right. During the swinging process, the swing arm assembly 4 pushes the brake caliper assembly 5 under test, and through the push rod 404, realizes the left and right sliding of the piston of the brake caliper assembly 5, simulating the actual working state.

[0088] During the test, the PLC control system collects the rotation parameters of servo motor 2 and the pressure curve of the hydraulic device in real time. By comparing them with preset values, dynamic compensation is performed to ensure that the actual swing parameters and hydraulic values ​​always approach the set standard. When servo motor 4 completes the preset number of rotations at the set frequency, and when servo motor 2 completes the preset number of rotations at the set frequency, the test automatically ends.

[0089] If the piston seal is good, the pressure curve of the hydraulic device should closely match the set curve. If there is slow pressure rise (due to seal leakage preventing rapid pressure build-up), abnormal pressure fluctuations (due to seal sticking causing poor oil flow), or poor sealing when the piston returns to its original position after pressure relief, it indicates that the piston's sealing performance is insufficient under dynamic operating conditions and cannot meet the actual working requirements.

[0090] The test system in this embodiment can effectively simulate the actual working state of the drum brake caliper assembly 5 during vehicle braking, effectively verify the reliability of piston sealing under dynamic conditions, and achieve relatively accurate test results.

[0091] The above descriptions are merely some embodiments of this application and are not intended to limit this application. The technical features or structures in the foregoing different embodiments can be arbitrarily combined to form other specific technical solutions as needed. For those skilled in the art, this application can have various modifications and variations. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principle of this application should be included within the protection scope of the claims of this application.

Claims

1. A testing apparatus suitable for testing the piston sealing performance of a brake caliper assembly (5), characterized in that: It includes a base (1), a drive unit disposed on the base (1), a swing arm assembly (4) hinged to the base (1), and a transmission unit disposed between the drive unit and the swing arm assembly (4); The base (1) is provided with a mounting part for mounting the brake caliper assembly (5). The drive part can drive the swing arm assembly (4) to swing through the transmission part and make the swing arm assembly (4) push the piston to move along its own axis.

2. The testing apparatus according to claim 1, characterized in that: The swing arm assembly (4) includes two swing arms (401) spaced apart to form a receiving space, and a connecting arm (402) hinged between one end of the two swing arms (401). The other ends of the two swing arms (401) are hinged to the base (1), and the brake caliper assembly (5) installed through the mounting part extends into the receiving space so that the pistons on both sides are pushed by the corresponding swing arms (401).

3. The testing apparatus according to claim 2, characterized in that: Each of the aforementioned swing arms (401) includes a swing arm body and a push rod (404) disposed on the swing arm body. The push rod (404) protrudes into the receiving space and can be inserted into the piston, thus restricting the piston from rotating about its own axis.

4. The testing apparatus according to claim 3, characterized in that: The push rod (404) is screwed onto the swing arm body; The piston has a groove (5011) at its end, and the push rod (404) can be inserted into the groove (5011). The push rod (404) has a limiting surface (4041) that abuts against the side wall of the groove (5011) to restrict the piston from rotating around its own axis.

5. The testing apparatus according to claim 4, characterized in that: The swing arm body is provided with a sleeve (403), the push rod (404) is screwed into the sleeve (403), and a nut is screwed onto the push rod (404), the nut abutting against the sleeve (403).

6. The testing apparatus according to claim 5, characterized in that: The sleeve (403) is screwed onto the swing arm body, and a limiting member (405) is provided on the swing arm body. The limiting member (405) is used to limit the rotation of the sleeve (403) relative to the swing arm body.

7. The testing apparatus according to any one of claims 2 to 6, characterized in that: The transmission unit includes an eccentric wheel (7) disposed on the drive shaft (201) of the drive unit. The drive unit is used to output rotational power, and the eccentric wheel (7) rotates with the drive shaft (201) to push each of the swing arms (401) to swing.

8. The testing apparatus according to claim 7, characterized in that: The transmission unit includes a bearing sleeved on the eccentric wheel (7), the bearing being located within the receiving space and abutting against the swing arms (401) on both sides; The eccentric wheel (7) pushes each of the swing arms (401) to swing through the bearing.

9. The testing apparatus according to claim 8, characterized in that: Each of the swing arms (401) is provided with a protruding portion (4011) that protrudes into the receiving space. The bearing abuts against the protrusions (4011) of the two swing arms (401).

10. A testing system, characterized in that: The test apparatus includes any one of claims 1 to 9, and a hydraulic device for connecting to the brake caliper assembly (5).

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