Turntable bearing experiment table
By designing the double-arm bridge structure of the rotary bearing test bench and using loading and rotating mechanisms, the problem that the bearing test bench cannot apply axial force or overturning moment in the prior art is solved, and accurate measurement and data support of the dynamic performance of the bearing is achieved.
Patent Information
- Application Number
- CN202510620780.8
- Authority / Receiving Office
- CN · China
- Patent Type
- Applications(China)
- Current Assignee / Owner
- Filing Date
- 2025-05-14
- Publication Date
- 2025-08-01
AI Technical Summary
The existing bearing test bench cannot apply axial force or overturning moment alone, resulting in the experimental data being only static data, which is difficult to reflect the dynamic performance of the bearing. The double-arm bridge mount requires auxiliary bearing rotation, and the measurement results show a micro-deformation error between the roller and the raceway.
A rotating wheel bearing experiment bench is designed, adopting a double-arm bridge structure, and the bearing is applied to the loading mechanism and the rotation mechanism, and combined with the detection component to measure deformation, the dynamic performance of the bearing under different load conditions is realized.
It realizes flexible simulation and accurate measurement of bearings under different load conditions, significantly improves experimental accuracy and provides reliable data support for bearing dynamic performance.
Smart Images
Figure CN120404140A_ABST
Abstract
Description
Technical Field
[0001] This application belongs to the technical field of bearing testing, and more specifically, relates to a turntable bearing test bench. Background Art
[0002] Bearings are important components in mechanical equipment. Their main function is to support rotating mechanical bodies, reduce the friction coefficient during their movement, and ensure their rotational accuracy. The quality of their performance directly affects and determines the performance of mechanical equipment. Therefore, it is necessary to test the deformation of each part of the bearing under complex external load conditions.
[0003] The test bench with a single-arm frame in the prior art has a simple structure and convenient operation. However, this test bench cannot apply axial force or overturning moment alone and cannot rotate the bearing, resulting in the experimental data being only static data, which limits the research on dynamic performance. There is also a design with a double-arm bridge frame, which overcomes the limitation of the single-arm frame in applying a single load and can apply axial force, radial force, and overturning moment arbitrarily. However, in addition to the test bearing, this test bench also requires an accompanying bearing to assist in rotation, which results in the measurement results being the data after the coupling of the two bearings. Due to the coupling effect, the observation error of the micro-deformation between the rollers and the raceway is relatively large, and it is difficult to reflect the true performance of the bearing. Summary of the Invention
[0004] To achieve the above object, the technical solution adopted in this application is:
[0005] A turntable bearing test bench includes a base, a lower flange cylinder, an upper flange cylinder, and a detection component. The lower flange cylinder is fixedly connected to the base. The upper flange cylinder and the lower flange cylinder are used to connect the outer ring and the inner ring of the test bearing respectively. Support arms are symmetrically arranged on both sides of the upper flange cylinder. A loading mechanism and a rotating mechanism are arranged at one end of each support arm away from the upper flange cylinder. The loading mechanism is used to apply a load to the test bearing, the rotating mechanism is used to drive the upper flange cylinder to rotate, and the detection component is used to measure the deformation of the test bearing.
[0006] Optionally, the loading mechanism includes an oil cylinder. One end of the oil cylinder is hinged to the support arm, and the other end is hinged to the rotating mechanism.
[0007] Optionally, the rotating mechanism includes an arc-shaped slide rail. A sliding carriage is slidably arranged on the slide rail. The sliding carriage is hinged to one end of the oil cylinder. A driving component is arranged on the base and is used to drive the sliding carriage to slide on the slide rail.
[0008] Optionally, push plates are arranged on both sides of the oil cylinder. The lower end of the push plate is fixedly connected to the sliding carriage, and the top of the push plate abuts against the support arm and is located on both sides of the support arm respectively.
[0009] Optionally, a pressure sensor is disposed between the push plate and the support arm.
[0010] Optionally, the drive assembly includes a motor, an output shaft of the motor is connected with a gear, an arc rack is disposed on the sliding carriage, and an arc of the arc rack is the same as an arc of the slide rail, and the gear meshes with the arc rack.
[0011] Optionally, an upper adapter flange and a lower adapter flange are further included, the upper adapter flange is provided with a plurality of first bearing connection holes arranged in a ring and a plurality of upper flange cylinder connection holes, and the lower adapter flange is provided with a plurality of second bearing connection holes arranged in a ring and a plurality of lower flange cylinder connection holes.
[0012] Optionally, a first mounting hole communicating with an inner cavity thereof is disposed on the upper flange cylinder, the upper adapter flange is provided with a second mounting hole and a third mounting hole penetrating through a thickness direction thereof, the second mounting hole and the third mounting hole respectively correspond to positions of an outer ring and an inner ring of the test bearing, and the third mounting hole is located inside the upper flange cylinder.
[0013] Optionally, the detection assembly includes an eddy current displacement sensor and an annular pressure sensor, the number of the eddy current displacement sensors is one or more and is used for measuring a bending deformation of a raceway of the test bearing; the annular pressure sensor is used for measuring a pre-tightening force of a bolt for fixing the test bearing and a pre-tightening force loss value.
[0014] Optionally, a plurality of rib plates are disposed on a side wall of the lower flange cylinder.
[0015] Compared with the prior art, the beneficial effects of the slewing bearing test bench provided by the present application are as follows:
[0016] In this application, the inner and outer rings of the experimental bearing are fixed by the lower flange cylinder and the upper flange cylinder. Support arms are symmetrically arranged on both sides of the upper flange cylinder, and a loading mechanism is arranged at the end of the support arm to apply a load to the bearing. When the two loading mechanisms provide tensile forces simultaneously, the deformation of the bearing raceway can be simulated under the condition that the bearing is only subjected to axial force; when one loading mechanism provides a tensile force and the other loading mechanism provides a thrust of the same magnitude, the deformation of the bearing raceway can be simulated under the condition that the bearing is only subjected to an overturning moment; when the two loading mechanisms provide tensile forces of different magnitudes, the deformation of the bearing raceway can be simulated under the condition that the bearing is simultaneously subjected to axial force and overturning moment. The bearing can be driven to rotate through a small angle by a rotating mechanism, and the deformation data of the experimental bearing is measured and recorded by a detection component. This application adopts a double-arm bridge structure to ensure the flexibility and diversity of load application. The upper flange cylinder is driven to rotate by a rotating mechanism, so that the micro-deformation between the roller and the raceway can be accurately measured, significantly improving the experimental accuracy. While ensuring the reliability of experimental data, it provides a new technical support for the research on the dynamic performance of bearings. BRIEF DESCRIPTION OF THE DRAWINGS
[0017] In order to more clearly illustrate the technical solutions in the embodiments of the present application, the following will briefly introduce the drawings required for use in the embodiments or the description of the prior art. Obviously, the following drawings are only some embodiments of the present application. For those of ordinary skill in the art, other drawings can be obtained based on these drawings without creative efforts.
[0018] Figure 1 is a schematic structural diagram of the slewing bearing test bench provided by the embodiment of the present application;
[0019] Figure 2 is a schematic cross-sectional structural diagram of the slewing bearing test bench provided by the embodiment of the present application;
[0020] Figure 3 is Figure 2 an enlarged schematic diagram of part A in
[0021] Figure 4 is a schematic structural diagram of the upper transfer flange in the slewing bearing test bench provided by the embodiment of the present application;
[0022] Figure 5 is a schematic structural diagram of the lower transfer flange in the slewing bearing test bench provided by the embodiment of the present application;
[0023] Figure 6 is a schematic principle diagram of the slewing bearing test bench provided by the embodiment of the present application when only axial load is applied;
[0024] Figure 7 is a schematic principle diagram of the slewing bearing test bench provided by the embodiment of the present application when axial load and overturning moment are applied simultaneously;
[0025] Among them, the reference numerals in the figures are as follows:
[0026] 1. Base; 2. Bottom plate; 3. Lower flange cylinder; 4. Lower adapter flange; 5. Test bearing; 6. Upper adapter flange; 7. Upper flange cylinder; 8. Support arm; 9. Oil cylinder; 10. Push plate; 11. Slide rail; 12. Sliding seat; 13. Motor; 14. Gear; 15. Arc rack; 16. Motor bracket; 17. First mounting hole; 18. Second mounting hole; 19. Third mounting hole; 20. First bearing connection hole; 21. Upper flange cylinder connection hole; 22. Lower flange cylinder connection hole; 23. Second bearing connection hole. Specific embodiments
[0027] In order to make the technical problems, technical solutions and beneficial effects to be solved by the present application clearer, the present application will be further described in detail below with reference to the drawings and embodiments. It should be understood that the specific embodiments described herein are only used to explain the present application and are not used to limit the present application.
[0028] It should be noted that when an element is referred to as being "fixed to" or "disposed on" another element, it can be directly on the other element or indirectly on the other element. When an element is referred to as being "connected to" another element, it can be directly connected to the other element or indirectly connected to the other element.
[0029] It should be understood that the orientation or positional relationship indicated by the terms "length", "width", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", etc. is based on the orientation or positional relationship shown in the drawings, and is only for the convenience of describing the present application and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be construed as a limitation to the present application.
[0030] In addition, the terms "first" and "second" are only used for descriptive purposes and cannot be construed as indicating or implying relative importance or implicitly indicating the quantity of the indicated technical features. Thus, the features defined with "first" and "second" may explicitly or implicitly include one or more of such features. In the description of the present application, "a plurality" means two or more unless specifically defined otherwise.
[0031] Please refer to Figures 1 - 7 , and now the turntable bearing test bench provided by the embodiment of the present application will be described.
[0032] A turntable bearing test bench, refer to Figure 1, including a base 1, a lower flange cylinder 3, an upper flange cylinder 7 and a detection component. The lower flange cylinder 3 is fixedly connected to the base 1. The upper flange cylinder 7 and the lower flange cylinder 3 are used to connect the outer ring and the inner ring of the experimental bearing 5 respectively. Support arms 8 are symmetrically arranged on both sides of the upper flange cylinder 7. A loading mechanism and a rotating mechanism are arranged at one end of each support arm 8 away from the upper flange cylinder 7. The loading mechanism is used to apply a load to the experimental bearing 5, and the rotating mechanism is used to drive the upper flange cylinder 7 to rotate. The detection component is used to measure the deformation of the experimental bearing 5.
[0033] In this application, the inner ring and the outer ring of the experimental bearing 5 are fixed by the lower flange cylinder 3 and the upper flange cylinder 7. Support arms 8 are symmetrically arranged on both sides of the upper flange cylinder 7. A load is applied to the bearing through the loading mechanism arranged at the end of the support arm 8. When the two loading mechanisms provide tensile forces simultaneously, the deformation of the bearing raceway under the condition that the bearing is only subjected to axial force can be simulated; when one side of the loading mechanism provides a tensile force and the other side provides a thrust force of the same magnitude, the deformation of the bearing raceway under the condition that the bearing is only subjected to an overturning moment can be simulated; when the two sides of the loading mechanism provide tensile forces of different magnitudes, the deformation of the bearing raceway under the condition that the bearing is simultaneously subjected to axial force and overturning moment can be simulated. The experimental bearing 5 can be driven to rotate by a small angle through the rotating mechanism, and the deformation data of the experimental bearing 5 are measured and recorded by the detection component. The double-arm bridge structure adopted in this application ensures the flexibility and diversity of load application. The upper flange cylinder 7 is rotated by the rotating mechanism, so that the micro-deformation between the roller and the raceway can be accurately measured, the experimental accuracy is significantly improved, and while ensuring the reliability of the experimental data, it provides a new technical support for the dynamic performance research of the bearing.
[0034] In some embodiments of this application, refer to Figure 1 , the loading mechanism includes an oil cylinder 9. One end of the oil cylinder 9 is hinged to the support arm 8, and the other end is hinged to the rotating mechanism.
[0035] By extending and retracting the oil cylinder 9, a force can be applied to the support arm 8, and the load is transmitted to the experimental bearing 5 through the support arm 8. Specifically, when the two oil cylinders 9 apply tensile forces to the support arm 8 simultaneously, the deformation of the bearing raceway under the condition that the experimental bearing 5 is only subjected to axial force can be simulated; when one side of the oil cylinder 9 provides a tensile force to the support arm 8 and the other side of the oil cylinder 9 provides a thrust force of the same magnitude to the support arm 8, the deformation of the raceway of the experimental bearing 5 under the condition that the experimental bearing 5 is only subjected to an overturning moment can be simulated; when the two oil cylinders 9 provide tensile forces of different magnitudes, the deformation of the bearing raceway under the condition that the experimental bearing 5 is simultaneously subjected to axial force and overturning moment can be simulated, realizing the flexibility and diversity of load application.
[0036] In some other embodiments of this application, other components can also be used for the loading mechanism, such as air cylinders, electric push rods, etc., and this application does not make any limitations.
[0037] In some embodiments of the present application, refer to Figure 1 , the rotating mechanism includes an arc-shaped slide rail 11, on which a sliding seat 12 is slidably arranged. One end of the sliding seat 12 is hinged to an oil cylinder 9, and a driving assembly for driving the sliding seat 12 to slide on the slide rail 11 is arranged on the base 1.
[0038] The driving assembly can drive the sliding seat 12 to slide along the arc-shaped slide rail 11, thereby driving the oil cylinder 9 and the support arm 8 to rotate, so as to drive the experimental bearing 5 to rotate at a small angle.
[0039] In some embodiments of the present application, refer to Figure 1 , push plates 10 are respectively arranged on both sides of the oil cylinder 9. The lower end of the push plate 10 is fixedly connected to the sliding seat 12, and the top of the push plate 10 abuts against the support arm 8 and is respectively located on both sides of the support arm 8.
[0040] Since the oil cylinder 9 and the support arm 8 are connected by an earring, if a rotational torque is directly provided to the support arm 8, there will be a thrust loss, resulting in an error in the measurement result. By arranging the push plates 10 on the sliding seat 12 and abutting the top of the push plates 10 against the support arm 8, when the driving assembly drives the sliding seat 12 to move, the sliding seat 12 can drive the push plates 10 to move, and the push plates 10 push the support arm 8 to rotate, thereby driving the experimental bearing 5 to rotate without thrust loss.
[0041] In some embodiments of the present application, a pressure sensor (not shown in the figure) is arranged between the push plate 10 and the support arm 8. By installing a pressure sensor on the push plate 10, the thrust torque provided by the push plate 10 to the support arm 8 can be measured, so as to measure the deformation trend of the bearing raceway under different thrust torques.
[0042] Specifically, two holes are arranged on each push plate 10 for installing the pressure sensor, and the number of pressure sensors is 8. The pressure sensor is mainly used to measure the thrust when the push plate 10 pushes the support arm 8 to calculate the pushing torque.
[0043] In some embodiments of the present application, refer to Figure 1 , the driving assembly includes a motor 13, the output shaft of the motor 13 is connected with a gear 14, an arc-shaped rack 15 is arranged on the sliding seat 12, and the radian of the arc-shaped rack 15 is the same as that of the slide rail 11, and the gear 14 meshes with the arc-shaped rack 15.
[0044] Specifically, the motor 13 is installed on the base 1 through a motor bracket 16. The motor 13 can drive the gear 14 to rotate, thereby driving the arc-shaped rack 15 to rotate. The arc-shaped rack 15 can drive the connected sliding seat 12 to slide on the slide rail 11, and the sliding seat 12 transmits the thrust to the support arm 8 through the push plate 10 to realize the function of driving the support arm 8 to rotate.
[0045] In some embodiments of the present application, referring to Figures 1 - 5 , it further includes an upper adapter flange 6 and a lower adapter flange 4. The upper adapter flange 6 is provided with a plurality of first bearing connection holes 20 arranged in a ring and a plurality of upper flange cylinder connection holes 21. The lower adapter flange 4 is provided with a plurality of second bearing connection holes 23 arranged in a ring and a plurality of lower flange cylinder connection holes 22.
[0046] The upper adapter flange 6 is used to connect the upper flange cylinder 7 and the upper contact surface of the test bearing 5. There are two circles of bolt holes distributed on the upper adapter flange 6 (the first bearing connection holes 20 and the upper flange cylinder connection holes 21 respectively). In this embodiment, the upper flange cylinder connection holes 21 are located in the inner circle and are used to connect the upper flange cylinder 7, and the first bearing connection holes 20 are located in the outer circle and are used to connect the outer ring of the test bearing 5. Similarly, there are two circles of bolt holes distributed on the lower adapter flange 4 (the second bearing connection holes 23 and the lower flange cylinder connection holes 22 respectively). In this embodiment, the second bearing connection holes 23 are located in the inner circle and are used to connect the inner ring of the test bearing 5, and the lower flange connection holes are located in the outer circle and are used to connect the lower flange cylinder 3. When it is necessary to study the influence of the distribution of the fixing bolts of the slewing bearing on the bearing capacity, the test bearing needs to change parameters such as the position and size of the fixing bolt holes. Therefore, when using test bearings 5 with different bolt hole positions and sizes for experiments, only the upper adapter flange 6 and the lower flange adapter need to be replaced, avoiding the replacement of the upper flange cylinder 7 and the lower flange cylinder 3, and having stronger applicability.
[0047] In some other embodiments of the present application, the connection positions of the upper adapter flange 6 and the lower adapter flange 4 with the test bearing 5 can also be exchanged, that is, the upper adapter flange 6 is connected to the inner ring of the test bearing 5, and the lower adapter flange 4 is connected to the outer ring of the test bearing 5.
[0048] In some embodiments of the present application, referring to Figure 3 , the upper flange cylinder 7 is provided with a first mounting hole 17 communicating with its inner cavity. The upper adapter flange 6 is provided with a second mounting hole 18 and a third mounting hole 19 penetrating through its thickness direction. The second mounting hole 18 and the third mounting hole 19 respectively correspond to the positions of the outer ring and the inner ring of the test bearing 5, and the third mounting hole 19 is located inside the upper flange cylinder 7.
[0049] In some embodiments of the present application, the detection assembly includes an eddy current displacement sensor, a pressure sensor, and an annular pressure sensor.
[0050] The eddy current displacement sensor is mainly used to measure the bending deformation of the raceway of the experimental bearing 5. The number of installed sensors can be set according to needs. If it is necessary to measure the continuous and complete cycle data of the roller-raceway deformation, as many sensors as possible should be installed. If it is only used for measuring the deformation during the rolling cycle of a single ball, only one eddy current sensor needs to be installed. The same applies to the eddy current displacement sensors at other positions, such as the lower raceway.
[0051] Specifically, refer to 2, Figure 3 and Figure 7 , where some of the eddy current displacement sensors can pass through the first mounting hole 17 and be installed into the second mounting hole 18, and some of the eddy current displacement sensors are installed in the third mounting hole 19. Avoidance holes corresponding to the positions of the third mounting holes 19 are provided on the flange of the upper flange cylinder 7. Refer to Figure 7 , some of the eddy current displacement sensors can be directly installed from the outside below the experimental bearing 5 to measure the bending deformation of the lower raceway of the outer ring of the experimental bearing 5. The annular pressure sensor is used to measure the pre-tightening force of the bolts (not shown in the figure) connecting the experimental bearing 5, the upper flange adapter plate 6, and the lower flange adapter plate 4, as well as the pre-tightening force loss value. Two to three annular pressure sensors can be installed in each of the vertical and parallel directions of the direction of the applied overturning moment.
[0052] In some embodiments of the present application, refer to Figure 1 , the lower flange cylinder 3 is fixedly connected to the base 1 through the bottom plate 2, and multiple rib plates are provided on the side wall of the lower flange cylinder 3. The lower flange cylinder 3 mainly plays a load-bearing role and needs to bear a pressure of at least 40t downward from the loading mechanism. Therefore, increasing the wall thickness of the lower flange cylinder 3 and providing rib plates on the outside of the lower flange cylinder 3 can improve its bearing capacity.
[0053] Experimental principle:
[0054] Refer to Figure 6 , since the inner ring of the experimental bearing 5 is directly connected to the base 1 and the deformation is very small, it can be ignored. Thus, the overall deformation Δ0 of the outer ring of the experimental bearing can be measured. The fixed frame of the eddy current displacement sensor is installed on the outer ring of the adapter plate, and then the bending deformation δ of the upper raceway of the outer ring of the experimental bearing is measured through the eddy current displacement sensor 1上 . Then the contact deformation between the rollers and the raceway of the experimental bearing can be calculated by Δ0 - δ 1上 .
[0055] Refer to Figure 7 , when an overturning moment and an axial load are applied simultaneously, one end of the upper row of rollers of the experimental bearing 5 is pressed tightly and the other end is in a relaxed state. At this time, the main stressed part of the relaxed end is the auxiliary thrust. The situation of the pressed end is similar to that when only the axial load is applied and can be measured by analogy.
[0056] The deformation of the loose end is relatively complex, and it generally shows an upward deformation trend.
[0057] Δ0 = δ 1下 +δ 2下 -δ 1上 -δ 2上
[0058] Among them, δ 1上 is the bending deformation of the upper raceway on the outer ring of the test bearing 5, and δ 1下 is the bending deformation of the lower raceway on the outer ring of the test bearing 5. δ 2上 , δ 2下 are the total contact deformations between the upper and lower raceways and the rollers. And δ 1上 , δ 2上 are very small and can be ignored.
[0059] Therefore, the contact deformation of the lower raceway can also be measured at this time.
[0060] Test steps:
[0061] 1. Assemble the test bearing 5 and install sensors (pressure sensors, eddy current displacement sensors, annular pressure sensors, etc.).
[0062] 2. After the assembly of the test bearing 5 is completed, check the pre-tightening of all bolts, especially the fixing bolts of the bearing, and measure the pre-tightening force with a torque wrench.
[0063] 3. Check the installation of the sensors and connect the motor 13 and the console.
[0064] [[ID=4...]]
[0065] 5. The two oil cylinders 9 simultaneously provide tensile forces to simulate the deformation of the bearing raceway when the bearing is only subjected to axial force. The motor 13 drives the gear 14 to provide a small-angle rotation, and read and record the data of each sensor.
[0066] 6. One oil cylinder 9 provides a tensile force, and the other oil cylinder 9 provides an equal thrust to simulate the deformation of the bearing raceway when the bearing is only subjected to an overturning moment. The motor 13 drives the gear 14 to provide a small-angle rotation, and read and record the sensor data.
[0067] 7. One oil cylinder 9 provides a smaller tensile force, and one oil cylinder 9 provides a larger tensile force to simulate the deformation of the bearing raceway when the bearing is simultaneously subjected to axial force and overturning moment. The motor 13 drives the gear 14 to provide a small-angle rotation, and read and record the data of each sensor.
[0068] 8. Replace the experimental bearing 5, the upper adapter flange 6 and the lower adapter flange 4, repeat steps 5, 6, and 7, and record the data.
[0069] In the solution of this application, when different magnitudes of tensile forces are provided by the loading mechanisms on both sides, the deformation of the bearing raceway can be simulated under the condition that the bearing is simultaneously subjected to an axial force and an overturning moment. The bearing can be driven to rotate at a small angle by the rotating mechanism, and the deformation data of the experimental bearing can be measured and recorded by the detection component. The double-arm bridge structure adopted in this application ensures the flexibility and diversity of load application. By driving the upper flange cylinder to rotate through the rotating mechanism, the micro-deformation between the roller and the raceway can be accurately measured, significantly improving the experimental accuracy. While ensuring the reliability of the experimental data, it provides new technical support for the research on the dynamic performance of the bearing.
[0070] The above are only the preferred embodiments of this application and are not intended to limit this application. Any modifications, equivalent replacements, improvements, etc. made within the spirit and principle of this application shall be included within the protection scope of this application.
Claims
1. A turntable bearing test bench, characterized in that: It includes a base, a lower flange cylinder, an upper flange cylinder and a detection assembly. The lower flange cylinder is fixedly connected to the base. The upper flange cylinder and the lower flange cylinder are used to connect the outer ring and the inner ring of the experimental bearing respectively. Support arms are symmetrically arranged on both sides of the upper flange cylinder. A loading mechanism and a rotating mechanism are arranged at one end of each support arm away from the upper flange cylinder. The loading mechanism is used to apply a load to the experimental bearing, and the rotating mechanism is used to drive the upper flange cylinder to rotate. The detection assembly is used to measure the deformation of the experimental bearing.
2. The turntable bearing test bench according to claim 1, wherein: The loading mechanism includes an oil cylinder. One end of the oil cylinder is hinged to the support arm, and the other end is hinged to the rotating mechanism.
3. The turntable bearing test bench according to claim 2, characterized in that: The rotating mechanism includes an arc-shaped slide rail. A sliding carriage is slidably arranged on the slide rail. The sliding carriage is hinged to one end of the oil cylinder. A driving assembly is arranged on the base for driving the sliding carriage to slide on the slide rail.
4. The turntable bearing test bench according to claim 3, wherein: Push plates are arranged on both sides of the oil cylinder. The lower end of the push plate is fixedly connected to the sliding carriage, and the top of the push plate abuts against the support arm and is located on both sides of the support arm respectively.
5. The turntable bearing test bench according to claim 4, characterized in that: A pressure sensor is arranged between the push plate and the support arm.
6. The turntable bearing test bench according to claim 3, wherein: The driving assembly includes a motor. The output shaft of the motor is connected with a gear. An arc-shaped rack is arranged on the sliding carriage, and the radian of the arc-shaped rack is the same as that of the slide rail. The gear meshes with the arc-shaped rack.
7. The turntable bearing test bench according to claim 1, characterized in that: It also includes an upper adapter flange and a lower adapter flange. The upper adapter flange is provided with a plurality of first bearing connection holes arranged in a ring and a plurality of upper flange cylinder connection holes. The lower adapter flange is provided with a plurality of second bearing connection holes arranged in a ring and a plurality of lower flange cylinder connection holes.
8. The turntable bearing test bench according to claim 7, wherein: The upper flange cylinder is provided with a first mounting hole communicating with its inner cavity. The upper adapter flange is provided with a second mounting hole and a third mounting hole penetrating through its thickness direction. The second mounting hole and the third mounting hole correspond to the positions of the outer ring and the inner ring of the experimental bearing respectively, and the third mounting hole is located inside the upper flange cylinder.
9. The turntable bearing test bench according to claim 8, wherein: The detection assembly includes an eddy current displacement sensor and an annular pressure sensor. The number of eddy current displacement sensors is one or more, which is used to measure the bending deformation of the raceway of the experimental bearing. The annular pressure sensor is used to measure the pre-tightening force of the bolts for fixing the experimental bearing and the pre-tightening force loss value.
10. The turntable bearing test bench according to claim 1, characterized in that: A plurality of rib plates are arranged on the side wall of the lower flange cylinder.