A dynamic friction coefficient measuring device and measuring method for semi-floating ring bearing

Abstract

The application discloses a kind of dynamic friction coefficient measuring device and measuring method for semi-floating ring bearing, belong to the technical field of friction coefficient measurement, including shafting component, power drive mechanism and tension sensor, shafting component includes sliding optical axis and corresponding half floating ring bearing base assembly and sliding optical axis support assembly being sleeved on sliding optical axis, and half floating ring bearing base assembly and sliding optical axis support assembly are fixedly supported on rack base in correspondence;Power drive mechanism is correspondingly set in one end of shafting component, and is driven connection with sliding optical axis by synchronous belt;Tension sensor is correspondingly set in one end of half floating ring bearing base assembly, and is driven connection with half floating ring bearing base assembly by traction line, for detecting the tangential direction tension in the rotating process of sliding optical axis.The dynamic friction coefficient measuring device of the application can satisfy the dynamic friction coefficient measurement of semi-floating ring bearing, and can efficiently and accurately measure dynamic friction coefficient.

Description

Technical Field

[0001] This invention relates to the field of friction coefficient measurement technology, and in particular to a dynamic friction coefficient measuring device and method for semi-floating ring bearings. Background Technology

[0002] In engineering and scientific research, the measurement of the coefficient of friction typically relies on a range of traditional methods and apparatus. One common method is the use of a friction testing machine, which measures the coefficient of friction by applying force between two test objects and measuring the resistance to their relative motion. However, this method is complex, requiring expensive instruments and cumbersome data analysis, increasing both experimental costs and technical barriers. Another common method is the inclined plane test, where test objects are placed on an inclined plane, and the coefficient of friction is calculated by measuring their sliding speed and the angle of inclination. While relatively simple, this method also has limitations. First, it requires high accuracy and repeatability of the coefficient of friction, necessitating precise measuring equipment and instrument calibration. Second, the inclined plane test may not be suitable for certain special cases, such as measuring materials with very low coefficients of friction or handling non-uniform surfaces, and the accuracy and repeatability of the results can be affected by the operator's skill and experience, potentially leading to inconsistent test results. Furthermore, some dynamic coefficient of friction measurement devices use standard friction coefficient specimens, measuring the coefficient by applying the specimen to the test surface and measuring the required force. Traditional methods for measuring the coefficient of friction are very useful in some situations, but they are difficult to apply to measuring the coefficient of friction in some special structures.

[0003] Semi-floating ring bearings, as a type of hydrodynamic bearing, have a wedge-shaped clearance between the bearing shell and the journal. The rotation of the main shaft drives the flow of lubricating oil, forming a pressure oil film, thus achieving lubrication and load-bearing functions. As a supporting component, they are widely used in high-speed, light-load rotating machinery due to their high rotational accuracy at high speeds, high operational stability, low frictional power consumption, and low heat generation. However, because the oil film pressure of semi-floating ring bearings dynamically changes with speed, load, and lubrication conditions during operation, and the wedge-shaped clearance between the bearing shell and the journal is extremely small, they are highly sensitive to the flow and pressure distribution of lubricating oil, making the measurement of their dynamic friction coefficient extremely difficult. Currently, existing dynamic friction coefficient measuring devices mainly use boundary friction and translational friction methods to measure the dynamic friction coefficient, which are difficult to apply to the measurement of dynamic friction coefficient in high-speed rotating machinery such as semi-floating ring bearings. Summary of the Invention

[0004] Technical problem solved: In view of the technical problems existing in the measurement of the dynamic friction coefficient of semi-floating ring bearings in the prior art, the present invention provides a dynamic friction coefficient measuring device and method for semi-floating ring bearings, which can efficiently and accurately measure the dynamic friction coefficient of semi-floating ring bearings.

[0005] Technical solution: The present invention provides a dynamic friction coefficient measuring device for semi-floating ring bearings, the measuring device comprising:

[0006] A shaft system assembly, comprising a sliding optical shaft and a semi-floating ring bearing base assembly and a sliding optical shaft support assembly correspondingly mounted on the sliding optical shaft, wherein the semi-floating ring bearing base assembly and the sliding optical shaft support assembly are fixedly supported on a platform base.

[0007] A power drive mechanism is correspondingly disposed at one end of the shaft system assembly and is connected to the sliding optical shaft via a synchronous belt.

[0008] A tension sensor is disposed at one end of the semi-floating ring bearing base assembly and is connected to the semi-floating ring bearing base assembly via a traction line. It is used to detect the tangential tension during the rotation of the sliding optical axis.

[0009] Preferably, the semi-floating ring bearing base assembly includes a bearing base outer frame and a floating inner frame that is vertically slidably connected within the bearing base outer frame. The two ends of the floating inner frame are respectively fastened with a first transparent oil reservoir and a second transparent oil reservoir.

[0010] A pressure sensor is provided at the bottom inner side of the bearing base outer frame, corresponding to the lower side of the floating inner frame. Guide baffles are provided longitudinally on both outer sides of the bearing base outer frame to restrict the floating inner frame inside the bearing base outer frame.

[0011] The floating inner frame is fixedly equipped with a deep groove ball bearing and an oil supply outer copper sleeve fitted inside the inner ring of the deep groove ball bearing. Both ends of the oil supply outer copper sleeve are sealed with oil supply outer copper sleeve retaining rings. One end of the oil supply outer copper sleeve is equipped with an oil pipe joint, and the top end of the other end of the oil supply outer copper sleeve is equipped with a limit screw.

[0012] A semi-floating ring bearing is provided inside the oil supply outer copper sleeve along its axial direction, and the two ends of the semi-floating ring bearing are restricted inside the oil supply outer copper sleeve by bearing retaining rings.

[0013] Preferably, the pressure sensor includes a second sensor base and a pressure-bearing probe fixedly mounted on the second sensor base, and the pressure-bearing probe is electrically connected to the control system.

[0014] Preferably, the tensile sensor includes a first sensor base and a tensile test shaft fixedly disposed on its upper end. The tensile test shaft is arranged parallel to the sliding optical axis, and a connecting hole is provided at the front end of the tensile test shaft. The connecting hole is fixedly connected to one end of the traction line, and the other end of the traction line passes through the second transparent oil reservoir and is fixedly connected to the limiting screw. The traction line is arranged perpendicular to the tensile test shaft and the sliding optical axis.

[0015] Preferably, the sliding optical axis support assembly includes a sliding bearing base fixedly connected to the platform base, a sliding bearing for the sliding optical axis to pass through is provided in the sliding bearing base, a third transparent oil storage tank is provided at both ends of the sliding bearing, and an oil outlet is provided at the lower end of the third transparent oil storage tank.

[0016] Preferably, the platform base is provided with multiple interconnected oil storage tanks, and the platform base is provided with U-shaped oil storage pans corresponding to the first transparent oil storage tank, the second transparent oil storage tank and the third transparent oil storage tank.

[0017] Preferably, a counterweight disk assembly is fitted at both ends of the sliding optical shaft. The counterweight disk assembly includes a counterweight disk that is slidably fitted on the sliding optical shaft. A wheel pawl fitted on the sliding optical shaft is fixedly connected to one side of the counterweight disk. A locking sleeve is threaded to the end of the wheel pawl away from the counterweight disk. Rotating the locking sleeve on the side closer to the counterweight disk can lock the wheel pawl on the sliding optical shaft.

[0018] Preferably, the shaft system assembly further includes a transmission pulley assembly correspondingly disposed at one end of the sliding optical shaft. The transmission pulley assembly includes two sets of rolling bearing bases correspondingly disposed. The rolling bearing base includes a base frame fixedly disposed on the platform base and rolling bearings installed in the base frame. The inner rings of the two sets of rolling bearings are fixedly connected to a pulley shaft. One end of the pulley shaft is fixedly connected to one end of the sliding optical shaft through a diaphragm coupling. A second synchronous pulley is fixedly connected to the pulley shaft.

[0019] Preferably, the power drive mechanism includes a motor base and a drive motor fixedly mounted thereon, and a first synchronous pulley is provided at the power shaft end of the drive motor. The first synchronous pulley and the second synchronous pulley are connected by a synchronous belt drive.

[0020] This invention also discloses a method for measuring the coefficient of kinetic friction, the method comprising:

[0021] Step 1: After assembling the measuring device, install it on the ground in the designated area;

[0022] Step 2: Start the drive motor according to the preset program. The drive motor drives the first synchronous pulley to rotate through the frequency converter. The first synchronous pulley drives the pulley shaft to rotate through the synchronous belt and the second synchronous pulley. The pulley shaft drives the sliding optical shaft to rotate synchronously through the diaphragm coupling. During the rotation of the sliding optical shaft, the lubricating oil in the gap of the semi-floating ring bearing is driven to flow. The lubricating oil generates an oil film force to balance the load force based on the dynamic pressure effect and pushes up the journal of the sliding optical shaft, so that the journal of the sliding optical shaft is separated from the inner surface of the semi-floating ring bearing. This causes the floating inner frame that fixes the semi-floating ring bearing to move up and down relative to the outer frame of the bearing base. During this process, the pressure sensor records the sum of the compressive load force and the weight of the floating inner frame and its internal components. Subtracting the known weight of the floating inner frame and its internal components, the radial load force W generated during the rotation of the sliding optical shaft can be obtained.

[0023] Step 3: During the rotation of the sliding optical shaft, the frictional force generated by the shear stress on the surface of the sliding optical shaft journal by the lubricating oil causes the semi-floating ring bearing to generate a horizontal tension in the opposite direction to the frictional force. Since the semi-floating ring bearing is tightly fitted with the oil supply outer copper sleeve, this tension is transmitted to the oil supply outer copper sleeve, causing it to have a tendency to rotate or to rotate. The tension is transmitted to the tension sensor through the traction line wound on the limit screw. The tension sensor records the tension value during this process, which is the dynamic friction force f.

[0024] Step 4: The friction coefficient μ can be obtained by using the friction coefficient calculation formula μ=f / W.

[0025] Compared with the prior art, the present invention has the following beneficial effects:

[0026] 1. The dynamic friction coefficient measuring device of the present invention can meet the dynamic friction coefficient measurement of semi-floating ring bearings, and can efficiently and accurately measure the dynamic friction coefficient;

[0027] 2. The power drive mechanism and shaft system are set separately, which can reduce the impact of vibration generated by the high-speed rotation of the drive motor on the test bench base, and help improve the measurement accuracy of dynamic friction coefficient;

[0028] 3. This diaphragm coupling connects the sliding optical shaft and the pulley shaft. It relies on the elastic deformation of the diaphragm to compensate for the relative displacement of the two shafts. It has a significant elastic damping effect and high transmission efficiency. It can effectively avoid mutual interference between the sliding optical shaft and the pulley shaft. Compared with gear couplings, it can better compensate for the adverse effects caused by misalignment of the two shafts.

[0029] 4. The semi-floating ring bearing base assembly has an ingenious structure. It uses a method of measuring the tension that balances the frictional force to obtain the frictional force of the lubricating oil on the surface of the sliding optical shaft journal, which solves the problem of the difficulty in accurately measuring the frictional performance of the semi-floating ring bearing base.

[0030] 5. The base structure of this test stand is stable and reliable, with good vibration absorption performance, and can collect overflowing lubricating oil, making it suitable for the high-speed operating environment of semi-floating ring bearings;

[0031] 6. The counterweight plate assembly provides counterweight for the sliding optical axis, reducing the adverse effects of vibration during the rotation of the sliding optical axis on the detection results. Attached Figure Description

[0032] Figure 1 This is a first-view three-dimensional structural diagram of the measuring device according to an embodiment of the present invention;

[0033] Figure 2 for Figure 1 A schematic diagram of the second-view three-dimensional structure of the measuring device;

[0034] Figure 3 for Figure 1 Schematic diagram of the three-dimensional structure of the shaft system assembly of the measuring device;

[0035] Figure 4 for Figure 3 A top view of the shaft system assembly;

[0036] Figure 5 for Figure 4 Cross-sectional view of the central axis assembly along line AA;

[0037] Figure 6 for Figure 3 Schematic diagram of the three-dimensional structure of the measurement component;

[0038] Figure 7 for Figure 6 Top view of the measurement component structure;

[0039] Figure 8 for Figure 7 Sectional view of the BB section of the measurement component;

[0040] Figure 9 for Figure 6 Schematic diagram of the connection structure between the semi-floating ring bearing base assembly and the sliding optical shaft;

[0041] Figure 10 for Figure 9 Cross-sectional view of the axial structure of the semi-floating ring bearing base assembly and the sliding optical shaft;

[0042] Figure 11 for Figure 9 Schematic diagram of the internal structure of the semi-floating ring bearing base assembly;

[0043] Figure 12 for Figure 9 Schematic diagram of the internal structure of the outer copper bushing of the oil supply system;

[0044] Figure 13 for Figure 12 Schematic diagram of the exploded structure of the outer copper sleeve of the oil supply unit;

[0045] Figure 14 for Figure 11 Schematic diagram of the three-dimensional structure of the medium pressure sensor;

[0046] Figure 15 for Figure 3 Schematic diagram of the three-dimensional structure of the central drive pulley assembly;

[0047] Figure 16 for Figure 3 A schematic diagram of the three-dimensional structure of a tension sensor.

[0048] Reference numerals: 100, Measuring device; 1, Bench base; 2, Shaft assembly; 3, Synchronous belt; 4, Power drive mechanism; 5, Drive motor; 6, Motor base; 7, Oil accumulator; 8, First synchronous pulley; 9, Tension sensor; 91, First sensor base; 92, Tension test shaft; 93, Connecting hole; 10, Oil tank; 11, Transmission pulley assembly; 111, Belt pulley shaft; 112, Rolling bearing base; 1121, Base frame; 1122, Rolling bearing; 113, Second synchronous pulley; 12, Diaphragm coupling; 13, Traction line; 14, Sliding optical shaft; 15, Semi-floating ring bearing base assembly; 151, Bearing base outer... 152. Frame; 153. Floating inner frame; 154. Guide baffle; 155. First transparent oil reservoir; 156. Mounting hole; 157. Oil supply outer copper sleeve; 158. Oil pipe joint; 159. Second transparent oil reservoir; 150. Deep groove ball bearing; 1510. Limiting screw; 1511. Bearing retaining ring; 1512. Semi-floating ring bearing; 16. Sliding optical shaft support assembly; 161. Sliding bearing base; 162. Sliding bearing; 163. Third transparent oil reservoir; 17. Counterweight plate assembly; 171. Counterweight plate; 172. Wheel chuck; 173. Locking sleeve; 18. Pressure sensor; 181. Second sensor base; 182. Pressure probe. Detailed Implementation

[0049] To make the objectives, technical solutions, and advantages of the embodiments of the present invention clearer, the following will be described in conjunction with the accompanying drawings. Figures 1-16 The technical solutions of the embodiments of the present invention are clearly and completely described. Obviously, the described embodiments are only a part of the embodiments of the present invention, not all of them. All other embodiments obtained by those skilled in the art based on the described embodiments of the present invention are within the scope of protection of the present invention.

[0050] Example 1: As Figures 1-5As shown, the present invention provides a dynamic friction coefficient measuring device for a semi-floating ring bearing. The measuring device 100 includes a shaft assembly 2, a power drive mechanism 4, and a tension sensor 9. The shaft assembly 2 includes a sliding optical shaft 14 and a semi-floating ring bearing base assembly 15 and a sliding optical shaft support assembly 16, which are respectively mounted on the sliding optical shaft 14. The semi-floating ring bearing base assembly 15 and the sliding optical shaft support assembly 16 are respectively fixedly supported on the test bench base 1, that is, the sliding bearing 162 is rotatably connected between the semi-floating ring bearing base assembly 15 and the sliding optical shaft support assembly 16.

[0051] like Figures 9-13 As shown, the semi-floating ring bearing base assembly 15 includes a bearing base outer frame 151 and a floating inner frame 152 vertically slidably connected within the bearing base outer frame 151. The two ends of the floating inner frame 152 are respectively fastened with a first transparent oil reservoir 154 and a second transparent oil reservoir 158. The first transparent oil reservoir 154 has several holes of different sizes, located above and below the first transparent oil reservoir 154. The upper hole of the first transparent oil reservoir 154 is an oil inlet hole to facilitate the connection of an oil pipe, and the lower hole is an oil outlet hole of the semi-floating ring bearing base assembly 15. The second transparent oil reservoir 158 has holes on both sides for the traction line 13 to pass through, and its lower end is also provided with an oil outlet hole. Guide baffles 153 are longitudinally arranged on both sides of the outer frame 151 of the bearing base. The guide baffles 153 restrict the floating inner frame 152 inside the outer frame 151 of the bearing base, allowing the floating inner frame 152 to float relative to the outer frame 151 of the bearing base in the vertical direction.

[0052] A deep groove ball bearing 159 and an oil supply outer copper sleeve 156 fitted inside the inner ring of the deep groove ball bearing 159 are fixedly installed inside the floating inner frame 152. The oil supply outer copper sleeve 156 can rotate along the axis of the floating inner frame 152 through the deep groove ball bearing 159. Oil supply outer copper sleeve retaining rings are sealed at both ends of the oil supply outer copper sleeve 156, and the oil supply outer copper sleeve retaining rings can activate the sealing function. An oil pipe joint 157 is provided at one end of the oil supply outer copper sleeve 156, and the oil pipe joint 157 is connected to an external oil supply hose, so that lubricating oil can enter the oil supply outer copper sleeve 156. A limit screw 1510 is provided at the top of the other end of the oil supply outer copper sleeve 156. The limit screw 1510 can satisfy the fixed connection of the traction line 13, so that when the oil supply outer copper sleeve 156 rotates, the tangential tension generated by it is transmitted to the tension sensor 9 through the traction line 13. A semi-floating ring bearing 1512 is arranged axially inside the oil supply outer copper sleeve 156. The semi-floating ring bearing 1512 is the bearing to be tested. Both ends of the semi-floating ring bearing 1512 are restricted inside the oil supply outer copper sleeve 156 by bearing retaining rings 1511. This arrangement of the semi-floating ring bearing 1512 only allows it to rotate relative to the oil supply outer copper sleeve 156, avoiding axial movement that would affect the measurement effect of the dynamic friction coefficient.

[0053] like Figure 11 and Figure 14 As shown, a pressure sensor 18 is provided at the bottom inner side of the bearing base outer frame 151, corresponding to the lower side of the floating inner frame 152. The pressure sensor 18 includes a second sensor base 181 and a pressure probe 182 fixedly mounted on the second sensor base 181. The sensor base is fixedly connected to the bearing base outer frame 151, and the pressure probe 182 is supported on the ground of the floating inner frame 152. During the process of the floating inner frame 152 floating up and down along the bearing base outer frame 151, the pressure load force can be applied to the pressure probe 182. The pressure probe 182 is electrically connected to the control system. The control system can use existing technology to realize data storage, analysis and other functions to record the pressure load force data detected by the pressure probe 182.

[0054] like Figure 4 and Figure 16 As shown, the tension sensor 9 is correspondingly disposed at one end of the semi-floating ring bearing base assembly 15. The tension sensor 9 includes a first sensor base 91 and a tension test shaft 92 fixedly disposed at its upper end. The tension test shaft 92 is arranged parallel to the sliding optical axis 14, and a connecting hole 93 is provided at the front end of the tension test shaft 92. The connecting hole 93 is fixedly connected to one end of the traction line 13. The other end of the traction line 13 passes through the hole of the second transparent oil reservoir 158 and is fixedly connected to the limiting screw 1510. The traction line 13 is arranged perpendicularly to the tension test shaft 92 and the sliding optical axis 14. During the rotation of the sliding optical shaft 14, the frictional force generated by the shear stress on the journal surface of the sliding optical shaft 14 causes the semi-floating ring bearing 1512 to generate a horizontal tension in the opposite direction to the frictional force. Since the semi-floating ring bearing 1512 is in close contact with the oil supply outer copper sleeve 156, the tension is transmitted to the oil supply outer copper sleeve 156, causing it to have a tendency to rotate or to rotate. The tension is transmitted to the tension sensor 9 via the traction line 13 wound on the limit screw 1510, and the tension sensor 9 can record the tension value.

[0055] like Figures 7-8As shown, the sliding optical axis support assembly 16 includes a sliding bearing base 161 fixedly connected to the platform base 1. A sliding bearing 162 for the sliding optical axis 14 to pass through is provided inside the sliding bearing base 161. An oil inlet hole is provided above the sliding bearing base 161. A third transparent oil reservoir 163 is provided at both ends of the sliding bearing 162. An oil outlet hole is provided at the lower end of the third transparent oil reservoir 163. The sliding optical axis support assembly 16 provides stable support for the sliding optical axis 14 during operation. Multiple interconnected oil storage tanks 10 are arranged on the plate surface of the test bench base 1. U-shaped oil storage pans 7 are arranged on the test bench base 1 corresponding to the first transparent oil storage tank 154, the second transparent oil storage tank 158 and the third transparent oil storage tank 163. An oil outlet is provided on the front side of the oil storage pan 7, which is connected to the oil supply pump (not shown in the figure) through an oil supply hose. The oil can be recycled through the oil supply pump. The oil leakage generated during the test can be stored in the oil storage tanks 10, which not only improves the working environment at the work site, but also realizes the recycling of oil.

[0056] Counterweight disk assemblies 17 are fitted at both ends of the sliding optical axis 14. The counterweight disk assembly 17 includes a counterweight disk 171 that is slidably fitted on the sliding optical axis 14. A wheel pawl 172 fitted on the sliding optical axis 14 is fixedly connected to one side of the counterweight disk 171. A locking sleeve 173 is threaded to the end of the wheel pawl 172 away from the counterweight disk 171. Rotating the locking sleeve 173 on the side closer to the counterweight disk 171 can lock the wheel pawl 172 on the sliding optical axis 14. The position of the counterweight disk assembly 17 on the sliding optical axis 14 can be adjusted as needed and can be easily fixed. The counterweight disk assembly 17 provides counterweight for the sliding optical axis 14, reducing the adverse effect of vibration during the rotation of the sliding optical axis 14 on the detection results.

[0057] like Figures 1-3 and Figure 15As shown, the shaft assembly 2 also includes a transmission pulley assembly 11 correspondingly disposed at one end of the sliding optical shaft 14. The transmission pulley assembly 11 includes two sets of rolling bearing bases 112 correspondingly disposed. The rolling bearing base 112 includes a base frame 1121 fixedly disposed on the platform base 1 and rolling bearings 1122 installed in the base frame 1121. The inner rings of the two sets of rolling bearings 1122 are fixedly connected to a pulley shaft 111. One end of the pulley shaft 111 is fixedly connected to one end of the sliding optical shaft 14 through a diaphragm coupling 12. A second synchronous pulley 113 is fixedly connected to the pulley shaft 111. The power drive mechanism 4 includes a motor base 6 and a drive motor 5 fixedly disposed on it. A first synchronous pulley 8 is disposed at the power shaft end of the drive motor 5. The first synchronous pulley 8 and the second synchronous pulley 113 are connected by a synchronous belt 3. The power drive mechanism 4 is connected to the transmission pulley assembly 11 via a synchronous belt 3, thereby realizing the rotation drive of the sliding optical shaft 14. The power drive mechanism 4 and the shaft assembly 2 are set separately, which can reduce the impact of the vibration generated by the high-speed rotation of the drive motor 5 on the test stand base 1, and is conducive to improving the measurement accuracy of the dynamic friction coefficient.

[0058] The installation method of the measuring device 100 of the present invention includes the following steps:

[0059] (a) The bearing base outer frame 151, the sliding bearing base 161, the rolling bearing base 112, the oil storage pan 7 and the sensor support are fixedly installed on the platform base 1.

[0060] (ii) Install the second synchronous pulley 113 in the center of the pulley shaft 111, and arrange the deep groove ball bearings 159 at the recesses at both ends of the pulley shaft 111; at the same time, one end of the pulley shaft 111 is fixedly connected to one end of the diaphragm coupling 12. It should be noted that the shaft end of the pulley shaft 111 should not extend too far into the diaphragm coupling 12; fix the deep groove ball bearings 159 connected to both ends of the pulley shaft 111 in the base frame 1121 respectively, thus completing the assembly of the transmission pulley assembly 11.

[0061] (iii) The motor base 6 is arranged on the ground on one side of the platform base 1. The drive motor 5 is fixedly connected to the motor base 6. The first synchronous pulley 8 is installed on the motor shaft of the drive motor 5. Then the first synchronous pulley 8 is connected to the second synchronous pulley 113 through the synchronous belt 3.

[0062] (iv) Install the pressure sensor 18 at the center of the bottom inner side of the bearing base outer frame 151. Support the floating inner frame 152 on the pressure sensor 18. Fix the guide baffle 153 to the outer sides of the bearing base outer frame 151 with screws to confine the floating inner frame 152 within the bearing base outer frame 151. Install the deep groove ball bearing 159 in the inner groove of the floating inner frame 152. Install the oil supply outer copper sleeve 156 on the inner ring of the deep groove ball bearing 159. Then install the oil supply outer copper sleeve retaining ring at both ends of the outer side of the oil supply outer copper sleeve 156. Install the oil pipe connector 157 at one end of the oil supply outer copper sleeve 156 and the limit screw 1510 at the other end. Then, a semi-floating ring bearing 1512 is arranged inside the oil supply outer copper sleeve 156, and the semi-floating ring bearing 1512 is fixed inside the oil supply outer copper sleeve 156 by placing a bearing retainer ring 1511 in the groove inside the oil supply outer copper sleeve 156, thus completing the installation of the semi-floating ring bearing base assembly 15.

[0063] (v) Arrange the sliding bearing 162 in the hole provided in the center of the sliding bearing base 161, then install the sliding bearing 162 cover in the recesses on both sides of the sliding bearing base 161, and install the third transparent oil reservoir 163 on both sides of the sliding bearing base 161 to complete the sliding optical axis support assembly 16.

[0064] (vi) The tension sensor 9 is set on the stand base 1 on one side of the semi-floating ring bearing base assembly 15. Then, one end of the traction line 13 is passed through the hole above the rear side of the second transparent oil reservoir 158 and fixedly connected to the limiting screw 1510. The other end of the traction line 13 is fixedly connected to the hole on the front side of the tension sensor 9. Finally, the first transparent oil reservoir 154 and the second transparent oil reservoir 158 are fixedly connected to the outer sides of both ends of the floating inner frame 152.

[0065] (vii) Assemble a set of counterweight disk assemblies 17 on one end of the sliding optical shaft 14, and then pass the other end of the sliding optical shaft 14 through the shaft hole provided in the center of the semi-floating ring bearing base assembly 15 and the sliding optical shaft support assembly 16 in sequence. Install another set of mass disk assemblies on the sliding optical shaft 14 accordingly, and then fix the sliding optical shaft 14 to the diaphragm coupling 12. The counterweight disk assembly 17 near the diaphragm coupling 12 does not come into contact with the diaphragm coupling 12, and the sliding optical shaft 14 does not easily extend too far into the diaphragm coupling 12.

[0066] (viii) Move and adjust the two sets of counterweight disk assemblies 17 to the appropriate position on the sliding optical axis 14 respectively, and then fix the position of the two sets of counterweight disk assemblies 17 by tightening the locking sleeve 173.

[0067] Example 2: The present invention also discloses a method for measuring the coefficient of kinetic friction, the method comprising:

[0068] Step 1: After assembling the measuring device 100, install it on the ground in a specific area.

[0069] Step 2: Start the drive motor 5 according to the preset program. The drive motor 5 drives the first synchronous pulley 8 to rotate via frequency conversion. The first synchronous pulley 8 drives the pulley shaft 111 to rotate via the synchronous belt 3 and the second synchronous pulley 113. The pulley shaft 111 drives the sliding optical shaft 14 to rotate synchronously via the diaphragm coupling 12. During the rotation of the sliding optical shaft 14, the lubricating oil in the gap of the semi-floating ring bearing 1512 flows. The lubricating oil generates an oil film force to balance the load force based on the dynamic pressure effect and pushes up the journal of the sliding optical shaft 14, so that the journal of the sliding optical shaft 14 separates from the inner surface of the semi-floating ring bearing 1512. This causes the floating inner frame 152 that fixes the semi-floating ring bearing 1512 to move up and down relative to the bearing base outer frame 151. During this process, the pressure sensor 18 records the sum of the compressive load force and the weight of the floating inner frame 152 and its internal components. Subtracting the known weight of the floating inner frame 152 and its internal components, the radial load force W generated during the rotation of the sliding optical shaft 14 can be obtained.

[0070] Step 3: During the rotation of the sliding optical shaft 14, the frictional force generated by the shear stress on the journal surface of the sliding optical shaft 14 causes the semi-floating ring bearing 1512 to generate a horizontal tension in the opposite direction to the frictional force. Since the semi-floating ring bearing 1512 is tightly fitted with the oil supply outer copper sleeve 156, the tension is transmitted to the oil supply outer copper sleeve 156, causing it to rotate or rotate. The tension is transmitted to the tension sensor 9 via the traction line 13 wound on the limit screw 1510. The tension sensor 9 records the tension value during this process, which is the dynamic friction force f.

[0071] Step 4: The friction coefficient μ can be obtained by using the friction coefficient calculation formula μ=f / W.

[0072] The above are preferred embodiments of the present invention. It should be noted that, for those skilled in the art, several improvements and modifications can be made without departing from the principle of the present invention, and these improvements and modifications should also be considered within the scope of protection of the present invention.

Claims

1. A device for measuring the dynamic friction coefficient of a semi-floating ring bearing, characterized in that, The measuring device (100) includes: The shaft system assembly (2) includes a sliding optical shaft (14) and a semi-floating ring bearing base assembly (15) and a sliding optical shaft support assembly (16) respectively fitted on the sliding optical shaft (14). The semi-floating ring bearing base assembly (15) and the sliding optical shaft support assembly (16) are fixedly supported on the platform base (1). The semi-floating ring bearing base assembly (15) includes a bearing base outer frame (151) and a floating inner frame (152) vertically slidably connected in the bearing base outer frame (151). The two ends of the floating inner frame (152) are respectively fastened with a first transparent oil reservoir (154) and a second transparent oil reservoir (158). A pressure sensor (18) is provided on the bottom inner side of the bearing base outer frame (151) and below the floating inner frame (152). Guide baffles (153) are provided longitudinally on the outer sides of both sides of the bearing base outer frame (151). The guide baffles (153) restrict the floating inner frame (152) inside the bearing base outer frame (151). The floating inner frame (152) is fixedly provided with a deep groove ball bearing (159) and an oil supply outer copper sleeve (156) fitted inside the inner ring of the deep groove ball bearing (159). The oil supply outer copper sleeve (156) is sealed with oil supply outer copper sleeve retaining rings at both ends. One end of the oil supply outer copper sleeve (156) is provided with an oil pipe joint (157), and the other end of the oil supply outer copper sleeve (156) is provided with a limit screw (1510). A semi-floating ring bearing (1512) is provided inside the oil supply outer copper sleeve (156) along its axial direction. Both ends of the semi-floating ring bearing (1512) are restricted inside the oil supply outer copper sleeve (156) by bearing retaining rings (1511). The sliding optical axis support assembly (16) includes a sliding bearing base (161) fixedly connected to the platform base (1). The sliding bearing base (161) is provided with a sliding bearing (162) through which the sliding optical axis (14) passes. The sliding bearing (162) is provided with a third transparent oil storage tank (163) at both ends. The lower end of the third transparent oil storage tank (163) is provided with an oil outlet hole. A power drive mechanism (4) is correspondingly disposed at one end of the shaft assembly (2) and is connected to the sliding optical shaft (14) via a synchronous belt (3); wherein, a counterweight disk assembly (17) is fitted at both ends of the sliding optical shaft (14), the counterweight disk assembly (17) includes a counterweight disk (171) slidably fitted on the sliding optical shaft (14), a wheel pawl (172) fitted on the sliding optical shaft (14) is fixedly connected to one side of the counterweight disk (171), and a locking sleeve (173) is threadedly connected to the end of the wheel pawl (172) away from the counterweight disk (171). Rotating the locking sleeve (173) close to the side of the counterweight disk (171) can lock the wheel pawl (172) on the sliding optical shaft (14); A tension sensor (9) is disposed at one end of the semi-floating ring bearing base assembly (15) and is connected to the semi-floating ring bearing base assembly (15) via a traction line (13) to detect the tangential tension during the rotation of the sliding optical axis (14).

2. The device for measuring the dynamic friction coefficient of a semi-floating ring bearing according to claim 1, characterized in that, The pressure sensor (18) includes a second sensor base (181) and a pressure probe (182) fixedly mounted on the second sensor base (181). The pressure probe (182) is electrically connected to the control system.

3. The device for measuring the dynamic friction coefficient of a semi-floating ring bearing according to claim 2, characterized in that, The tension sensor (9) includes a first sensor base (91) and a tension test shaft (92) fixedly installed at its upper end. The tension test shaft (92) is arranged parallel to the sliding optical axis (14), and a connection hole (93) is provided at the front end of the tension test shaft (92). The connection hole (93) is fixedly connected to one end of the traction line (13), and the other end of the traction line (13) passes through the second transparent oil reservoir (158) and is fixedly connected to the limiting screw (1510). The traction line (13) is arranged perpendicular to the tension test shaft (92) and the sliding optical axis (14).

4. The device for measuring the dynamic friction coefficient of a semi-floating ring bearing according to claim 1, characterized in that, The platform base (1) has multiple interconnected oil storage tanks (10) on its surface. The platform base (1) is provided with U-shaped oil storage pans (7) corresponding to the first transparent oil storage tank (154), the second transparent oil storage tank (158) and the third transparent oil storage tank (163).

5. The device for measuring the dynamic friction coefficient of a semi-floating ring bearing according to claim 1, characterized in that, The shaft assembly (2) also includes a transmission pulley assembly (11) correspondingly disposed at one end of the sliding optical shaft (14). The transmission pulley assembly (11) includes two sets of rolling bearing bases (112) correspondingly disposed. The rolling bearing base (112) includes a base frame (1121) fixedly disposed on the platform base (1) and rolling bearings (1122) installed in the base frame (1121). The inner rings of the two sets of rolling bearings (1122) are fixedly connected to a pulley shaft (111). One end of the pulley shaft (111) is fixedly connected to one end of the sliding optical shaft (14) through a diaphragm coupling (12). A second synchronous pulley (113) is fixedly connected to the pulley shaft (111).

6. The device for measuring the dynamic friction coefficient of a semi-floating ring bearing according to claim 5, characterized in that, The power drive mechanism (4) includes a motor base (6) and a drive motor (5) fixedly mounted thereon. The power shaft end of the drive motor (5) is provided with a first synchronous pulley (8). The first synchronous pulley (8) and the second synchronous pulley (113) are connected by a synchronous belt (3).

7. A method for measuring the coefficient of kinetic friction, characterized in that, Using the measuring device as described in claim 6, the measuring method includes: Step 1: After assembling the measuring device (100), install it on the ground in a specific area; Step 2: Start the drive motor (5) according to the preset program. The drive motor (5) drives the first synchronous pulley (8) to rotate via frequency conversion. The first synchronous pulley (8) drives the pulley shaft (111) to rotate via the synchronous belt (3) and the second synchronous pulley (113). The pulley shaft (111) drives the sliding optical shaft (14) to rotate synchronously via the diaphragm coupling (12). During the rotation of the sliding optical shaft (14), the lubricating oil in the gap of the semi-floating ring bearing (1512) is driven to flow. The lubricating oil generates an oil film force to balance the load force based on the dynamic pressure effect and lifts up the lubricating oil. The journal of the sliding optical shaft (14) is separated from the inner surface of the semi-floating ring bearing (1512), thereby causing the floating inner frame (152) that fixes the semi-floating ring bearing (1512) to move up and down relative to each other along the outer frame (151) of the bearing base. During this process, the pressure sensor (18) records the sum of the compressive load force, the weight of the floating inner frame (152) and its internal components, and subtracts the known weight of the floating inner frame (152) and its internal components to obtain the radial load force W generated during the rotation of the sliding optical shaft (14). Step 3: During the rotation of the sliding optical shaft (14), the friction force generated by the shear stress on the journal surface of the sliding optical shaft (14) causes the semi-floating ring bearing (1512) to generate a horizontal tension in the opposite direction to the friction force. Since the semi-floating ring bearing (1512) is tightly attached to the oil supply outer copper sleeve (156), the tension is transmitted to the oil supply outer copper sleeve (156) to cause it to rotate or rotate. The tension is transmitted to the tension sensor (9) through the traction line (13) wound on the limit screw (1510). The tension sensor (9) records the tension value during the process, which is the dynamic friction force f. Step 4: The friction coefficient μ can be obtained by using the friction coefficient calculation formula μ=f / W.

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