Test device for engineering machinery bearing and test method thereof
By setting up a monitoring space and rectangular groove between the test bearing housing and the bearing to be tested, placing sensors, and adopting a composite loading method, the problem of low detection accuracy of large-size bearings is solved, realizing high-precision multi-parameter monitoring and working condition simulation, which meets the requirements of performance evaluation and life prediction of engineering machinery bearings.
Patent Information
- Authority / Receiving Office
- CN · China
- Patent Type
- Applications(China)
- Current Assignee / Owner
- NORTHEASTERN UNIV FOSHAN GRADUATE SCHOOL OF INNOVATION
- Filing Date
- 2026-01-21
- Publication Date
- 2026-05-08
AI Technical Summary
When monitoring large-sized bearings, the sensors in existing engineering machinery bearing testing devices are far from the center of the bearing, which reduces the accuracy of experimental data and affects the testing precision.
A monitoring space is formed between the test bearing housing and the bearing to be tested. A rectangular slot is set up to place the monitoring sensor, which is located close to the spindle to improve data accuracy. A composite loading is achieved through axial and radial loading drive components to simulate the low-speed heavy load and dynamic fluctuation conditions of engineering machinery.
It enables simultaneous measurement of multiple parameters and real-time monitoring of operating status, improves detection accuracy, and can more realistically reproduce the service conditions of engineering machinery bearings, meeting the needs of performance evaluation and life prediction.
Smart Images
Figure CN121994483A_ABST
Abstract
Description
Technical Field
[0001] This invention relates to the field of testing equipment technology, and in particular to a testing apparatus and method for testing bearings of engineering machinery. Background Technology
[0002] Construction machinery bearings operate under complex loads and harsh conditions for extended periods, exhibiting characteristics such as diverse load types, large fluctuations, and strong environmental vibrations. In actual operation, construction machinery not only bears combined axial and radial loads but also experiences frequent start-stop cycles, low-speed heavy loads, and impact loads. These conditions cause complex dynamic responses in the bearings during operation, thus affecting their lifespan and reliability. Therefore, construction machinery bearings need to be effectively tested on a test bench before use to ensure their lifespan and reliability.
[0003] Existing engineering machinery bearings are generally tested using a testing device. Specifically, the entire testing device is placed on a workbench. The existing testing device includes a drive part, at least one test bearing assembly, and a test bearing assembly, which are arranged sequentially along the longitudinal direction of the workbench. The drive part, the test bearing assembly, and the test bearing assembly are coaxially arranged. It also includes a test spindle, one end of which is connected to the drive part, and the other end passes through the test bearing assembly and the test bearing assembly in sequence to complete the test.
[0004] Currently, to study the stress state, dynamic response, and performance degradation of bearings under real-world operating conditions, it is typically necessary to conduct loading and monitoring experiments using a dedicated bearing test bench. Existing monitoring methods involve attaching sensors to the circumferential sidewalls of the bearing housing to monitor the bearing. However, current monitoring methods are only suitable for smaller bearings. The main reason is that as bearings become larger, the bearing walls become thicker, resulting in a greater distance between the monitoring sensors and the center of the bearing, thus affecting the accuracy of the experimental data collected and reducing testing precision. Summary of the Invention
[0005] In view of the above-mentioned shortcomings and deficiencies of the prior art, the present invention provides a testing device and testing method for engineering machinery bearings, which solves the technical problem that once the bearing size is large, the bearing wall will also become thicker, which will cause the monitoring sensor to be far from the center of the bearing to be tested, thus affecting the accuracy of the experimental data collected by the sensor and reducing the detection accuracy.
[0006] To achieve the above objectives, the main technical solutions adopted by the present invention include: On one hand, embodiments of the present invention provide a testing apparatus for engineering machinery bearings, including a drive assembly, a test assembly, and a test body; The test assembly has at least one test bearing housing, the test body has a test bearing housing, and the test bearing housing and the test bearing housing are coaxially arranged. The test bearing housing is used to place the test bearing, and the test bearing housing is used to place the bearing to be tested. The output end of the drive assembly is connected to a spindle, and the end of the spindle passes through and is inserted into the test bearing and the bearing to be tested in sequence. A monitoring space is formed between the test bearing housing and the outer ring of the bearing to be tested, and the monitoring space is used to place the monitoring sensor.
[0007] Optionally, the monitoring space is a rectangular groove extending along the axial direction of the bearing housing. The rectangular groove is formed on the inner side wall of the test bearing housing and / or the outer side wall of the bearing to be tested, and the monitoring sensor is disposed in the rectangular groove.
[0008] Optionally, multiple rectangular grooves are provided, and the multiple rectangular grooves are spaced apart circumferentially along the inner sidewall of the test bearing housing and / or along the outer sidewall of the bearing to be tested.
[0009] Optionally, the rectangular groove is opened axially along the end face of the test bearing housing and / or the bearing to be tested, with an axial depth of 120mm-160mm, a radial length of 5mm-15mm, and a circumferential length of 8mm-15mm.
[0010] Optionally, the test body further includes a loading chamber, an axial loading drive, and a radial loading drive; The test bearing housing is disposed within the loading chamber. Both the axial loading drive and the radial loading drive are located outside the loading chamber. The axial loading drive is disposed on a first side of the loading chamber, and the radial loading drive is disposed on a fourth / second side of the loading chamber. The driving end of the axial loading drive passes through the first side and abuts against the bearing inside the test bearing housing, so as to provide axial loading force to the bearing under test. The driving end of the radial loading drive passes through the fourth / second side and abuts against a side wall of the test bearing housing, so as to provide radial loading force to the bearing under test.
[0011] Optionally, the loading box includes a bottom wall, a first side, a second side, a third side, and a fourth side arranged sequentially above the bottom wall; An inverted trapezoidal groove is provided on the third side surface. A second arc-shaped groove is provided at the bottom of the inverted trapezoidal groove for placing the second test bearing. The second arc-shaped groove is used to place the second test bearing as the second lower test bearing seat. A connecting end face is formed between the bottom of the inverted trapezoidal groove and the second arc-shaped groove. A second upper test bearing seat is detachably connected to the connecting end face.
[0012] Optionally, the test-accompanying component includes a first test-accompanying structural component and a second test-accompanying structural component; The second test component is located between the first test component and the test body. The first test component includes a first lower test bearing seat. The top of the first lower test bearing seat is provided with a first arc-shaped groove for placing the first test bearing. A first upper test bearing seat is detachably connected to the first lower test bearing seat.
[0013] Optionally, a torque sensor is provided between the drive assembly and the spindle.
[0014] Optionally, it also includes a worktable with a T-slot, and the drive assembly, the test mate assembly, and the test body are all detachably mounted on the worktable via a sliding plate.
[0015] On the other hand, a testing method for engineering machinery bearings: the testing method is based on the aforementioned testing apparatus for engineering machinery bearings, and the testing method includes the following steps: S1. Select the drive assembly and the accompanying assembly according to the bearing to be tested in the test body; S2. Install the drive assembly, the test assembly, and the test body onto the workbench in sequence; S3. Connect the main shaft to the drive assembly, and pass it through the test bearing of the test assembly and the test bearing of the test body in sequence. S4. Start the drive component and monitor the space through the monitoring sensors.
[0016] The beneficial effects of this invention are as follows: This invention provides a testing device and method for engineering machinery bearings. By forming a monitoring space between the bearing housing and the bearing under test, this monitoring space is used to place and monitor key response signals such as stress, strain, and acceleration of the outer ring. Because this monitoring space is closer to the spindle than the outer ring of the bearing housing, the detection results are more accurate. It enables simultaneous measurement of multiple parameters and real-time monitoring of operating conditions. It solves the limitations of existing research in terms of loading methods, monitoring techniques, and operating condition simulation: on the one hand, existing test benches mainly operate under unidirectional loading or high-speed constant speed conditions, which cannot reproduce the actual operating conditions of engineering machinery under low speed, heavy load, and dynamic fluctuations; on the other hand, the closed design of the bearing housing restricts in-situ measurement of key physical quantities such as stress, strain, and acceleration of the outer ring, resulting in the inability to obtain multi-parameter dynamic data of the bearing under actual operating conditions. Therefore, it meets the needs of performance evaluation, structural optimization, and life prediction of engineering machinery bearings. Attached Figure Description
[0017] Figure 1 This is a front-view perspective three-dimensional structural schematic diagram of the testing and experimental device for bearings of engineering machinery according to the present invention; Figure 2 for Figure 1 A top-view three-dimensional structural diagram (the top cover and the outer shell are not shown). Figure 3 This is a rear-view perspective of the testing apparatus for bearings of engineering machinery according to the present invention; Figure 4 for Figure 3 A top-view three-dimensional structural diagram (the top cover and the outer shell are not shown). Figure 5 for Figure 1 A schematic diagram of the structure of the test bearing housing of the test body; Figure 6 for Figure 5 Schematic diagram of the middle section (rectangular hole is opened in the outer ring of the bearing to be tested); Figure 7 for Figure 5 Schematic diagram of the middle section (rectangular hole is opened in the inner ring of the test bearing housing); Figure 8 The strain time-domain diagrams inside and outside the tank under an axial load of 30 kN are shown. Figure 9 The strain time-domain diagrams inside and outside the tank under an axial load of 50 kN are shown. Figure 10 Vibration comparison diagrams of the embodiment and the comparative example under different rotational speeds, with radial load of 50kN and axial load of 30kN.
[0018] Explanation of reference numerals in the attached figures 1. Drive assembly; 2. Test assembly; 21. First test bearing; 22. Second test bearing; 23. First test structural component; 231. First lower test bearing housing; 232. First arc-shaped groove; 233. First upper test bearing housing; 24. Second test structural component; 25. Test housing; 3. Test body; 31. Test bearing housing; 32. Bearing to be tested; 321. Inner ring; 322. Rolling element; 323. Outer ring; 33. Loading box; 331, bottom wall; 332, first side; 333, second side; 334, third side; 335, fourth side; 336, inverted trapezoidal groove; 337, second arc-shaped groove; 338, second upper test bearing seat; 339, top cover; 34, axial loading drive; 35, radial loading drive; 4, main shaft; 5, rectangular groove; 6, torque sensor; 7, worktable; 8, sliding plate; 9, monitoring sensor. Detailed Implementation
[0019] To better explain and facilitate understanding of the present invention, the present invention will be described in detail below with reference to the accompanying drawings and specific embodiments.
[0020] Example 1: See Figures 1-7 As shown in the embodiment of the present invention, a testing device for engineering machinery bearings includes a drive assembly 1, a test assembly 2, and a test body 3. The test assembly 2 has at least one test bearing housing, and the test body 3 has a test bearing housing 31, which are coaxially arranged. The test bearing housing is used to hold a test bearing, and the test bearing housing 31 is used to hold a bearing 32 to be tested. The output end of the drive assembly 1 is connected to a main shaft 4, and the end of the main shaft 4 passes through and is inserted into the test bearing and the bearing 32 to be tested in sequence. A monitoring space is formed between the test bearing housing 31 and the outer ring of the bearing 32 to be tested, and the monitoring space is used to place a monitoring sensor 9.
[0021] In this embodiment, a testing device and method for engineering machinery bearings are described. A monitoring space is formed between the test bearing housing 31 and the bearing 32 under test. This monitoring space is used to place and monitor key response signals such as stress, strain, and acceleration of the outer ring. Because this monitoring space is closer to the spindle 4, the detection results are more accurate. This enables simultaneous measurement of multiple parameters and real-time monitoring of operating status. It addresses the limitations of existing research in terms of loading methods, monitoring techniques, and operating condition simulation: on the one hand, existing test benches mainly operate under unidirectional loading or high-speed constant speed conditions, which cannot reproduce the actual operating conditions of engineering machinery under low speed, heavy load, and dynamic fluctuations; on the other hand, the closed design of the bearing housing restricts in-situ measurement of key physical quantities such as stress, strain, and acceleration of the outer ring, resulting in the inability to obtain multi-parameter dynamic data of the bearing under actual operating conditions. This ultimately meets the needs of performance evaluation, structural optimization, and life prediction of engineering machinery bearings.
[0022] Specifically, the test device features a rectangular groove 5 structure on the test bearing housing 31. This allows for the placement of various sensors, such as strain gauges and accelerometers, without compromising assembly accuracy or uniform force distribution, enabling real-time acquisition of multiple physical parameters of the outer ring of the bearing under test 32. Simultaneously, the bidirectional loading mechanism of the axial loading drive 34 and the radial loading drive 35 enables controllable axial and radial composite loading, allowing stable operation under low-speed and variable-speed conditions, thus more realistically reproducing the service conditions of engineering machinery bearings. Compared to existing technologies, the test device in this embodiment overcomes the technical bottlenecks of limited loading methods, restricted measurement means, and incomplete simulation of operating conditions, providing a more accurate and reliable experimental platform for performance evaluation, structural optimization, and life prediction of engineering machinery bearings. Furthermore, the rectangular groove 5 structure on the test bearing housing 31 is also suitable for testing intelligent bearings.
[0023] Furthermore, the monitoring space is a rectangular groove 5 extending along the axial direction of the bearing housing. The rectangular groove 5 is opened on the inner side wall of the test bearing housing 31 and / or the outer side wall of the bearing 32 to be tested. A monitoring sensor 9 is installed in the rectangular groove 5.
[0024] Furthermore, multiple rectangular grooves 5 are provided, and the multiple rectangular grooves 5 are spaced apart circumferentially along the inner sidewall of the test bearing seat 31 and / or along the outer sidewall of the bearing 32 to be tested.
[0025] Furthermore, the rectangular groove 5 is axially formed along the end face of the test bearing housing 31 and / or the bearing to be tested 32, with an axial depth of 120mm-160mm, a radial length of 5mm-15mm, and a circumferential length of 8mm-15mm. Preferably, it is formed along the end face of the test bearing housing 31 and / or the bearing to be tested 32, with an axial depth of 152mm, a radial length of 10mm, and a circumferential length of 13mm; six grooves are arranged at 86°, 176°, 221°, 266°, 311°, and 356°, with vertical upward as 0°. This parameter setting allows for closer proximity to the spindle 4, enabling more precise in-situ measurement of key physical quantities such as stress, strain, and acceleration of the bearing to be tested 32 during operation, which prevents the acquisition of multi-parameter dynamic data of the bearing under actual operating conditions.
[0026] Furthermore, the test body 3 also includes a loading housing 33, an axial loading drive 34, and a radial loading drive 35. The test bearing housing 31 is disposed within the loading housing 33. Both the axial loading drive 34 and the radial loading drive 35 are located outside the loading housing 33. The axial loading drive 34 is disposed on the first side 332 of the loading housing 33, and the radial loading drive 35 is disposed on the fourth side 335 / second side 333 of the loading housing 33. The driving end of the axial loading drive 34 passes through the first side 332 and abuts against the bearing inside the test bearing housing 31, thereby providing axial loading force to the bearing 32 under test. The driving end of the radial loading drive 35 passes through the fourth side 335 / second side 333 and abuts against one side wall of the test bearing housing 31, thereby providing radial loading force to the bearing 32 under test. In this embodiment, simultaneously, through a flexible axial and radial bidirectional loading mechanism, low-speed, heavy-load, and combined loads can be applied to the bearing, and it can operate stably under adjustable speed conditions, thus more realistically reproducing the service conditions of engineering machinery bearings. Furthermore, the platform should facilitate data acquisition and analysis, providing accurate and reliable experimental conditions for bearing performance testing, structural optimization, and life assessment. The load is applied in the form of thrust. The maximum thrust of both the axial and radial loading cylinders is 20t.
[0027] Furthermore, the loading box 33 includes a bottom wall 331 and a first side 332, a second side 333, a third side 334, and a fourth side 335 arranged sequentially above the bottom wall 331. The third side 334 has an inverted trapezoidal groove 336, and the bottom of the inverted trapezoidal groove 336 has a second arc-shaped groove 337 for placing the second test bearing 22. The second arc-shaped groove 337 is used to place the second test bearing 22 as a second lower test bearing seat, and the bottom of the inverted trapezoidal groove 336 and the second arc-shaped groove 337 form a connecting end face, and a second upper test bearing seat 338 is detachably connected to the connecting end face.
[0028] In addition, it also includes a transparent top cover 339, which is fastened to the loading box 33 with an open top, allowing the experimenters to clearly observe the experimental process.
[0029] Here, the bearing housings of the first test component 23 and the second test component 24 are both of a split type, and the main shaft 4 will be disassembled upwards as a whole. This facilitates the installation and disassembly of the main shaft 4. The second upper test bearing housing 338 on the side closer to the bearing to be tested 32 is directly integrated with the loading housing, which improves the stability of the second test component 24 on the side closer to the bearing to be tested 32 and is better suited for testing large-sized bearings to be tested 32. This prevents the large-sized bearing to be tested 32 from tipping over. Moreover, the axial force of the bearing to be tested 32 is borne by the second test bearing 22 of the second test component 24, so the axial force forms a closed loop in the loading housing 33. Therefore, the first test bearing 21 on the side closer to the drive assembly 1 (motor) is theoretically only subjected to radial force. The second test bearing 22 uses two tapered roller bearings installed face-to-face as the fixed end, and the first test bearing 21 uses a cylindrical roller bearing as the floating end.
[0030] Furthermore, the test component 2 includes a first test structure 23 and a second test structure 24. The second test structure 24 is located between the first test structure 23 and the test body 3. The first test structure 23 includes a first lower test bearing seat 231. The top of the first lower test bearing seat 231 is provided with a first arc-shaped groove 232 for placing the first test bearing 21. A first upper test bearing seat 233 is detachably connected to the first lower test bearing seat 231.
[0031] Furthermore, the test companion component 2 also includes a test companion shell 25 covering the first test companion structure 23 and the second test companion structure 24, which can protect the first test companion structure 23 and the second test companion structure 24.
[0032] Furthermore, a torque sensor 6 is installed between the drive assembly 1 and the spindle 4. The drive assembly 1 uses a 22kW servo spindle motor, which is connected to the torque sensor 6. The torque sensor 6 is directly connected to the spindle 4, allowing for better acquisition of the spindle 4's torque.
[0033] Furthermore, it also includes a worktable 7, on which a T-slot is provided. The drive assembly 1, the test component 2, and the test body 3 are all detachably mounted on the worktable 7 via a sliding plate 8. This facilitates adjustment of the axial positions of the drive assembly 1, the test component 2, and the test body 3, and makes installation and disassembly convenient.
[0034] A testing method for bearings of engineering machinery: The testing method is based on a testing apparatus for bearings of engineering machinery and includes the following steps: S1. Select drive assembly 1 and test assembly 2 according to the bearing to be tested in test body 3.
[0035] S2. Install the drive component 1, the test component 2, and the test body 3 onto the workbench 7 in sequence.
[0036] S3. Connect the main shaft 4 to the drive assembly 1, and pass it through the test bearing of the test assembly 2 and the test bearing of the test body 3 in sequence.
[0037] S4. Start the drive component 1 and monitor the space through the monitoring sensor 9.
[0038] Comparative Example 1: Unlike Example 1, the monitoring sensor is located on the outer peripheral sidewall of the bearing 32 under test. According to... Figures 8-9 It can be seen that, under the same rotational speed and load conditions, the amplitudes of strain and acceleration signals collected from the measuring points inside the tank are significantly higher than those from the measuring points outside the tank. Taking strain testing as an example, under the conditions of a rotational speed of 90 r / min and axial loads of 30 kN and 50 kN, the time-domain fluctuation amplitude of strain at the measuring points inside the tank is significantly greater than that at the corresponding outer measuring points, which can clearly reflect the enhanced strain response caused by load changes; while the strain amplitude changes at the outer measuring points are relatively limited, and the distinguishability of load changes is significantly reduced, indicating that the outer measuring signals are significantly attenuated during structural transmission.
[0039] See Figure 10 As shown, this difference is even more pronounced in acceleration tests. Under different rotational speeds (90 r / min, 180 r / min, 270 r / min) and different combinations of radial and axial loads, the peak value, peak-to-peak value, and effective value of the acceleration at the measuring points inside the groove show a clear increasing trend with changes in load and rotational speed. The effective value can reach approximately 1.3 to 2 times that of the measuring points outside the groove under high load conditions. In contrast, the effective value of the acceleration at the measuring points outside the groove varies less under different load conditions, with a limited overall fluctuation range, making it difficult to accurately reflect the impact of changes in operating conditions on the dynamic response of the bearing. This indicates that placing the monitoring sensor in the monitoring groove between the test bearing housing and the bearing under test can significantly reduce the impact of structural transmission attenuation on the test signal, improve the measurement sensitivity and resolution of physical quantities such as stress, strain, and vibration, and is particularly suitable for real-world performance testing of large-size engineering machinery bearings under low-speed, heavy-load conditions.
[0040] In the description of this invention, it should be understood that the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of indicated technical features. Therefore, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of this invention, "a plurality of" means two or more, unless otherwise explicitly specified.
[0041] In this invention, unless otherwise explicitly specified and limited, the terms "installation," "connection," "linking," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; 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; they can refer to the internal communication of two components or the interaction between two components. Those skilled in the art can understand the specific meaning of the above terms in this invention according to the specific circumstances.
[0042] In the description of this specification, the terms "one embodiment," "some embodiments," "embodiment," "example," "specific example," or "some examples," etc., refer to specific features, structures, materials, or characteristics described in connection with that embodiment or example, which are included in at least one embodiment or example of the present invention. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples. Moreover, without contradiction, those skilled in the art can combine and integrate the different embodiments or examples described in this specification, as well as the features of different embodiments or examples.
[0043] Although embodiments of the present invention have been shown and described above, it is understood that the above embodiments are exemplary and should not be construed as limiting the present invention. Those skilled in the art can make modifications, alterations, substitutions and variations to the above embodiments within the scope of the present invention.
Claims
1. A testing and experimental apparatus for bearings of engineering machinery, characterized in that: It includes a driving component (1), a test companion component (2), and a test body (3); The test assembly (2) has at least one test bearing seat, the test body (3) has a test bearing seat (31), and the test bearing seat and the test bearing seat (31) are coaxially arranged. The test bearing seat is used to place the test bearing, and the test bearing seat (31) is used to place the bearing to be tested (32). The output end of the drive assembly (1) is connected to the spindle (4), and the end of the spindle (4) passes through and is inserted into the test bearing and the bearing to be tested (32) in sequence. A monitoring space is formed between the test bearing housing (31) and the outer ring of the bearing to be tested (32), and the monitoring space is used to place the monitoring sensor (9).
2. The testing apparatus for engineering machinery bearings as described in claim 1, characterized in that: The monitoring space is a rectangular groove (5) extending along the axial direction of the bearing housing. The rectangular groove (5) is opened on the inner side wall of the test bearing housing (31) and / or the outer side wall of the bearing to be tested (32). The monitoring sensor (9) is installed in the rectangular groove (5).
3. The testing apparatus for engineering machinery bearings as described in claim 2, characterized in that: Multiple rectangular grooves (5) are provided, and the multiple rectangular grooves (5) are spaced apart circumferentially along the inner sidewall of the test bearing seat (31) and / or along the outer sidewall of the bearing to be tested (32).
4. The testing apparatus for engineering machinery bearings as described in claim 3, characterized in that: The rectangular groove (5) is opened along the end face of the test bearing seat (31) and / or the bearing to be tested (32) along its axial direction. The axial depth of the groove is 120mm-160mm, the radial length is 5mm-15mm, and the circumferential length is 8mm-15mm.
5. The testing apparatus for engineering machinery bearings as described in claim 1, characterized in that: The test body (3) also includes a loading box (33), an axial loading drive (34), and a radial loading drive (35). The test bearing housing (31) is disposed inside the loading box (33). The axial loading drive (34) and the radial loading drive (35) are both located outside the loading box (33). The axial loading drive (34) is disposed on the first side (332) of the loading box (33), and the radial loading drive (35) is disposed on the fourth side (335) / second side (333) of the loading box (33). The driving end of the axial loading drive (34) passes through the first side (332) and abuts against the bearing inside the test bearing housing (31) so as to provide axial loading force to the bearing (32) to be tested. The driving end of the radial loading drive (35) passes through the fourth side (335) / second side (333) and abuts against one side wall of the test bearing housing (31) so as to provide radial loading force to the bearing (32) to be tested.
6. The testing apparatus for engineering machinery bearings as described in claim 5, characterized in that: The loading box (33) includes a bottom wall (331), a first side (332), a second side (333), a third side (334) and a fourth side (335) arranged sequentially above the bottom wall (331); An inverted trapezoidal groove (336) is provided on the third side surface (334). A second arc-shaped groove (337) for placing the second test bearing (22) is provided at the bottom of the inverted trapezoidal groove (336). The second arc-shaped groove (337) is used to place the second test bearing (22) as the second lower test bearing seat. A connecting end face is formed between the bottom of the inverted trapezoidal groove (336) and the second arc-shaped groove (337). A second upper test bearing seat (338) is detachably connected to the connecting end face.
7. The testing apparatus for engineering machinery bearings as described in claim 6, characterized in that: The test companion component (2) includes a first test companion structure (23) and a second test companion structure (24); The second test component (24) is located between the first test component (23) and the test body (3). The first test component (23) includes a first lower test bearing seat (231). The top of the first lower test bearing seat (231) is provided with a first arc groove (232). The first arc groove (232) is used to place the first test bearing (21). The first lower test bearing seat (231) is detachably connected to a first upper test bearing seat (233).
8. The testing apparatus for engineering machinery bearings as described in claim 1, characterized in that: A torque sensor (6) is provided between the drive assembly (1) and the main shaft (4).
9. The testing apparatus for engineering machinery bearings as described in claim 1, characterized in that: It also includes a worktable (7), on which a T-slot is provided. The drive assembly (1), the test accompaniment assembly (2) and the test body (3) are all detachably installed on the worktable (7) via a sliding plate (8).
10. A testing method for bearings of engineering machinery: the testing method is based on the testing apparatus for bearings of engineering machinery according to any one of claims 1-9, and the testing method includes the following steps: S1. Select the drive assembly (1) and the test assembly (2) according to the bearing to be tested in the test body (3). S2. Install the drive assembly (1), the test accompaniment assembly (2) and the test body (3) sequentially on the workbench (7); S3. Connect the main shaft (4) to the drive assembly (1) and pass it through the test bearing of the test assembly (2) and the test bearing of the test body (3) in sequence. S4. Start the drive component (1) and monitor the space by monitoring the sensor (9).