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

Abstract

The invention discloses a dynamic friction coefficient measuring device and method for a semi-floating ring bearing, and belongs to the technical field of friction coefficient measurement. The dynamic friction coefficient measuring device comprises a shaft system assembly, a power driving mechanism and a tension sensor; the shaft system assembly comprises a sliding optical axis, and a semi-floating ring bearing base assembly and a sliding optical axis supporting assembly which are correspondingly sleeved on the sliding optical axis; the semi-floating ring bearing base assembly and the sliding optical axis supporting assembly are correspondingly and fixedly supported on the rack base; the power driving mechanism is correspondingly arranged at one end of the shafting assembly and is in transmission connection with the sliding optical shaft through a synchronous belt; the tension sensor is correspondingly arranged at one end of the semi-floating-ring bearing base assembly, is in transmission connection with the semi-floating-ring bearing base assembly through a pull wire and is used for detecting tangential tension in the rotating process of the sliding optical axis. The dynamic friction coefficient measuring device can meet the dynamic friction coefficient measurement of the semi-floating ring bearing, and can efficiently and accurately measure the dynamic friction coefficient.

Description

Technical Field

[0001] The invention relates to the technical field of friction coefficient measurement, and in particular to a dynamic friction coefficient measurement device and a measurement method for a semi-floating ring bearing. Background Art

[0002] In the field of engineering and scientific research, the measurement of friction coefficient usually relies on a series of traditional methods and devices. Among them, a common method is to use a friction tester, which measures the friction coefficient by applying force between two test objects and measuring the resistance to their relative motion. However, this method is complicated to operate and requires expensive instruments and cumbersome data analysis processes. These requirements not only increase the cost of the experiment, but also raise the technical threshold. Another common method is the inclined plane test, in which the test objects are placed on an inclined plane and the friction coefficient is calculated by measuring their sliding speed and inclination angle on the inclined plane. Although this method is relatively simple, it also has some limitations. First, it has high requirements for the accuracy and repeatability of the friction coefficient, requiring precise measurement equipment and instrument calibration; second, the inclined plane test may not be applicable to some special cases, such as materials with very low friction coefficients or materials with non-uniform surfaces, and the accuracy and repeatability of the results may be affected by the operator's skills and experience level, which may lead to inconsistent test results. In addition, there are some dynamic friction coefficient measurement devices that use standard friction coefficient standards to measure by applying the standards to the test surface and measuring the required force. The traditional friction coefficient measurement method is very useful in some cases, but it is difficult to apply it to the friction coefficient measurement of some special structures.

[0003] As a kind of hydrodynamic bearing, the semi-floating ring bearing has a wedge-shaped gap between the bearing shell and the journal. The rotation of the main shaft drives the flow of lubricating oil to form a pressure oil film, thereby achieving lubrication and load-bearing functions. As a supporting component, it has high rotation accuracy at high speeds, high operating stability, low friction power consumption, and low heat generation, and is widely used in high-speed, light-loaded rotating machinery. However, during the operation of the semi-floating ring bearing, the oil film pressure changes dynamically with speed, load and lubrication conditions, and the wedge-shaped gap between the bearing shell and the journal is very small, which is extremely sensitive to the flow and pressure distribution of the lubricating oil, making it extremely difficult to measure the dynamic friction coefficient. At present, the existing dynamic friction coefficient measurement device mainly uses boundary friction, translational friction and other methods to measure the dynamic friction coefficient, which is difficult to apply to the dynamic friction coefficient measurement of high-speed rotating machinery such as semi-floating ring bearings. Summary of the invention

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

[0005] Technical solution: The present invention provides a device for measuring the coefficient of dynamic friction of a semi-floating ring bearing, the device comprising: A shaft system assembly, the shaft system assembly includes a sliding optical axis and a semi-floating ring bearing base assembly and a sliding optical axis support assembly correspondingly sleeved on the sliding optical axis, the semi-floating ring bearing base assembly and the sliding optical axis support assembly correspondingly fixedly supported on the platform base; A power drive mechanism, which is correspondingly arranged at one end of the shaft system assembly and is connected to the sliding optical axis through a synchronous belt; The tension sensor is correspondingly arranged at one end of the semi-floating ring bearing base assembly and is transmission-connected to the semi-floating ring bearing base assembly through a traction line, and is used to detect the tangential tension during the rotation of the sliding optical axis.

[0006] Preferably, the semi-floating ring bearing base assembly comprises a bearing base outer frame and a floating inner frame vertically slidably connected in the bearing base outer frame, and the two ends of the floating inner frame are respectively buckled with a first transparent oil storage tank and a second transparent oil storage tank; The inner bottom of the bearing base outer frame is located at the lower side of the floating inner frame and is provided with a pressure sensor. The outer sides of the bearing base outer frame are longitudinally provided with guide baffles, which restrict the floating inner frame inside the bearing base outer frame. A deep groove ball bearing and an oil supply outer copper sleeve sleeved on the inner ring of the deep groove ball bearing are fixedly arranged in the floating inner frame, and both ends of the oil supply outer copper sleeve are sealed and connected with oil supply outer copper sleeve retaining rings; an oil pipe joint is arranged at one end of the oil supply outer copper sleeve, and a limiting screw is arranged at the top end of the other end of the oil supply outer copper sleeve; A semi-floating ring bearing is arranged in the oil supply outer copper sleeve along its axial direction, and both ends of the semi-floating ring bearing are restricted in the oil supply outer copper sleeve by bearing retaining rings.

[0007] Preferably, the pressure sensor comprises a second sensor base and a pressure probe fixedly arranged on the second sensor base, and the pressure probe is electrically connected to the control system.

[0008] Preferably, the tension sensor includes a first sensor base and a tension test axis fixedly arranged at the upper end thereof, the tension test axis is arranged parallel to the sliding optical axis, and a connecting hole is arranged at the front end of the tension test axis, the connecting hole is fixedly connected to one end of the traction line, the other end of the traction line passes through the second transparent oil storage tank and is fixedly connected to the limit screw, and the traction line is arranged vertically to the tension test axis and the sliding optical axis.

[0009] Preferably, the sliding optical axis support assembly includes a sliding bearing base fixedly connected to the stand base, a sliding bearing for the sliding optical axis to pass through is arranged in the sliding bearing base, third transparent oil storage tanks are correspondingly arranged at both ends of the sliding bearing, and an oil outlet hole is arranged at the lower end of the third transparent oil storage tank.

[0010] Preferably, a plurality of interconnected oil storage tanks are arranged on the disk surface of the stand base, and a U-shaped oil storage tank is arranged on the stand base corresponding to the first transparent oil storage tank, the second transparent oil storage tank and the third transparent oil storage tank.

[0011] Preferably, counterweight plate assemblies are correspondingly mounted at both ends of the sliding optical axis, and the counterweight plate assembly includes a counterweight plate that is slidably mounted on the sliding optical axis, a wheel claw that is fixedly connected to one side of the counterweight plate and is mounted on the sliding optical axis, and a locking sleeve is threadedly connected to the end of the wheel claw away from the counterweight plate, and the wheel claw can be locked on the sliding optical axis by rotating the locking sleeve close to the side of the counterweight plate.

[0012] Preferably, the shaft system assembly also includes a transmission pulley assembly correspondingly arranged at one end of the sliding optical axis, the transmission pulley assembly includes two corresponding sets of rolling bearing bases, the rolling bearing base includes a base frame fixedly arranged on the stand base and rolling bearings installed in the base frame, the inner rings of the two sets of rolling bearings are fixedly connected to the pulley shaft, one end of the pulley shaft is fixedly connected to one end of the sliding optical axis through a diaphragm coupling, and a second synchronous pulley is fixedly connected to the pulley shaft.

[0013] Preferably, the power drive mechanism comprises a motor base and a drive motor fixedly mounted thereon, a power shaft end of the drive motor is provided with a first synchronous belt pulley, and the first synchronous belt pulley is connected to the second synchronous belt pulley through a synchronous belt transmission.

[0014] The present invention also discloses a method for measuring a dynamic friction coefficient, the method comprising: Step 1: After assembling the measuring device, install it on the ground in a specific area; Step 2: Start the drive motor according to the preset program, and the drive motor drives the first synchronous pulley to rotate by frequency conversion. The first synchronous pulley drives the pulley shaft to rotate through the synchronous belt and the second synchronous pulley, and the pulley shaft drives the sliding optical axis to rotate synchronously through the diaphragm coupling; during the rotation of the sliding optical axis, the lubricating oil in the gap of the semi-floating ring bearing is driven to flow, and the lubricating oil generates an oil film force to balance the load force based on the dynamic pressure effect and lifts the journal of the sliding optical axis, so that the journal of the sliding optical axis and the inner surface of the semi-floating ring bearing are separated from each other, so that the floating inner frame fixing the semi-floating ring bearing moves up and down relatively along the outer frame of the bearing base. During this process, the pressure sensor records the sum of the compressive load force and the gravity of the floating inner frame and its internal components, and subtracts the known weight of the floating inner frame and its internal components to obtain the radial load force W generated during the rotation of the sliding optical axis; Step 3: During the rotation of the sliding optical axis, the friction force generated by the shear stress of the lubricating oil on the journal surface of the sliding optical axis causes the semi-floating ring bearing to generate a horizontal pulling force in the opposite direction that is balanced with the friction force. Since the semi-floating ring bearing fits tightly with the oil supply outer copper sleeve, the pulling force is transmitted to the oil supply outer copper sleeve to cause it to have a rotation tendency or rotation, and is transmitted to the tension sensor through the traction line wound on the limit screw. The tension sensor records the tension value in the process, that is, the dynamic friction force f; Step 4: The dynamic friction coefficient μ can be obtained by using the friction coefficient calculation formula μ=f / W.

[0015] Compared with the prior art, the present invention has the following beneficial effects: 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 measure the dynamic friction coefficient efficiently and accurately; 2. The power drive mechanism and the shaft system assembly are separated, which can reduce the impact of the vibration generated by the high-speed rotation of the drive motor on the test bench base, which is beneficial to improve the measurement accuracy of the dynamic friction coefficient; 3. The diaphragm coupling connects the sliding optical axis and the pulley shaft, and relies on the elastic deformation of the diaphragm to compensate for the relative displacement of the two connected shafts. It has obvious elastic vibration reduction effect and high transmission efficiency, and can effectively avoid mutual interference between the sliding optical axis and the pulley shaft. Compared with the gear coupling, it can better compensate for the adverse effects of the misalignment of the two axes; 4. The semi-floating ring bearing base assembly has an ingenious structure. It uses a method of obtaining the friction force of the lubricating oil on the surface of the journal of the sliding optical axis by measuring the tension that is balanced with the friction force, thus solving the problem that the friction performance of the semi-floating ring bearing base is difficult to accurately measure; 5. The test bench base structure is stable and reliable, with good vibration absorption performance, and can collect overflow lubricating oil, which is suitable for the high-speed operation environment of semi-floating ring bearings; 6. The counterweight plate assembly provides a counterweight for the sliding optical axis, reducing the adverse effects of vibration on the detection results during the rotation of the sliding optical axis. BRIEF DESCRIPTION OF THE DRAWINGS

[0016] Figure 1 It is a schematic diagram of the three-dimensional structure of the measuring device according to an embodiment of the present invention from a first viewing angle; Figure 2 for Figure 1 A schematic diagram of the second viewing angle of the stereoscopic structure of the measuring device; Figure 3 for Figure 1 Schematic diagram of the three-dimensional structure of the shaft system assembly of the measuring device; Figure 4 for Figure 3 A top view of the structure of the shaft system assembly; Figure 5 for Figure 4 AA structural section view of the center shaft assembly; Figure 6 for Figure 3 Schematic diagram of the three-dimensional structure of the measuring component; Figure 7 for Figure 6 A top view of the structure of the measuring component; Figure 8 for Figure 7 Structural cross-section view of the measuring component in the BB direction; Fig. 9 for Figure 6 Schematic diagram of the connection structure between the middle half floating ring bearing base assembly and the sliding optical axis; Fig.10 for Fig. 9 A cross-sectional view of the axial structure of the middle half floating ring bearing base assembly and the sliding optical axis; Fig.11 for Fig. 9 Schematic diagram of the internal structure of the middle half floating ring bearing base assembly; Fig.12 for Fig. 9 Schematic diagram of the internal structure of the outer copper sleeve of the oil supply; Fig.13 for Fig.12 Schematic diagram of the explosion structure of the outer copper sleeve of the central oil supply; Fig.14 for Fig.11 Schematic diagram of the three-dimensional structure of the medium pressure sensor; Fig.15 for Figure 3 Schematic diagram of the three-dimensional structure of the middle transmission pulley assembly; Fig.16 for Figure 3 Schematic diagram of the three-dimensional structure of the medium tension sensor.

[0017] Figure numerals: 100, measuring device; 1, bench base; 2, shaft system assembly; 3, synchronous belt; 4, power drive mechanism; 5, drive motor; 6, motor base; 7, oil storage tray; 8, first synchronous pulley; 9, tension sensor; 91, first sensor base; 92, tension test shaft; 93, connecting hole; 10, oil storage tank; 11, transmission pulley assembly; 111, 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 axis; 15, semi-floating ring bearing base assembly; 151, bearing base outer Frame; 152, floating inner frame; 153, guide baffle; 154, first transparent oil storage tank; 155, mounting hole; 156, oil supply outer copper sleeve; 157, oil pipe joint; 158, second transparent oil storage tank; 159, deep groove ball bearing; 1510, limit screw; 1511, bearing retaining ring; 1512, semi-floating ring bearing; 16, sliding optical axis support assembly; 161, sliding bearing base; 162, sliding bearing; 163, third transparent oil storage tank; 17, counterweight plate assembly; 171, counterweight plate; 172, wheel disc claw; 173, locking sleeve; 18, pressure sensor; 181, second sensor base; 182, pressure probe. DETAILED DESCRIPTION

[0018] To make the purpose, technical solution and advantages of the embodiments of the present invention clearer, the following will be combined with the attached Figures 1 to 16 The technical solutions of the embodiments of the present invention are described clearly and completely. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. Based on the described embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field belong to the scope of protection of the present invention.

[0019] Example 1: Figures 1 to 5 As shown, a dynamic friction coefficient measuring device for a semi-floating ring bearing of the present invention, the measuring device 100 includes a shaft system assembly 2, a power drive mechanism 4 and a tension sensor 9, the shaft system assembly 2 includes a sliding optical axis 14 and a semi-floating ring bearing base assembly 15 and a sliding optical axis support assembly 16 correspondingly mounted on the sliding optical axis 14, the semi-floating ring bearing base assembly 15 and the sliding optical axis support assembly 16 are correspondingly fixedly supported on the stand base 1, that is, the sliding bearing 162 is rotatably connected between the semi-floating ring bearing base assembly 15 and the sliding optical axis support assembly 16.

[0020] like Figures 9 to 13As 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 to the bearing base outer frame 151. The two ends of the floating inner frame 152 are respectively provided with a first transparent oil storage tank 154 and a second transparent oil storage tank 158. The first transparent oil storage tank 154 is provided with a plurality of holes of different sizes, which are respectively located above and below the first transparent oil storage tank 154. The upper hole of the first transparent oil storage tank 154 is an oil inlet hole for connecting an oil pipe, and the lower hole is an oil outlet hole of the semi-floating ring bearing base assembly 15; holes for the traction line 13 to pass through are provided on both sides of the second transparent oil storage tank 158, and an oil outlet hole is also provided at its lower end. Guide baffles 153 are longitudinally arranged 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, allowing the floating inner frame 152 to float in the up and down height direction relative to the bearing base outer frame 151.

[0021] A deep groove ball bearing 159 and an oil supply outer copper sleeve 156 mounted on the inner ring of the deep groove ball bearing 159 are fixedly arranged in 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; the 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 start the sealing function; an oil pipe joint 157 is arranged at one end of the oil supply outer copper sleeve 156, and the oil pipe joint 157 is connected to an external oil delivery hose, so that lubricating oil enters the oil supply outer copper sleeve 156, and a limiting screw 1510 is arranged on the top of the other end of the oil supply outer copper sleeve 156. The limiting screw 1510 can meet the fixed connection of the traction line 13, so that when the oil supply outer copper sleeve 156 rotates, the tangential direction tension generated by it is transmitted to the tension sensor 9 through the traction line 13. A semi-floating ring bearing 1512 is arranged along the axial direction inside the oil supply outer copper sleeve 156. The semi-floating ring bearing 1512 can be the bearing to be tested. Both ends of the semi-floating ring bearing 1512 are restricted in 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 affects the measurement effect of the dynamic friction coefficient.

[0022] like Fig.11 and Fig.14As shown, a pressure sensor 18 is correspondingly arranged at the bottom of the inner side of the bearing base outer frame 151 and at 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 arranged on the second sensor base 181. The sensor base is correspondingly fixedly connected to the bearing base outer frame 151, and the pressure probe 182 is correspondingly supported on the ground of the floating inner frame 152. When the floating inner frame 152 floats up and down along the bearing base outer frame 151, the compressive 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 the existing technology to realize data storage, analysis and other functions, and is used to record the compressive load force data detected by the pressure probe 182.

[0023] like Figure 4 and Fig.16 As shown, the tension sensor 9 is correspondingly arranged 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 arranged at its upper end. The tension test shaft 92 is arranged parallel to the sliding optical axis 14, and a connecting hole 93 is arranged 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 storage tank 158 and is fixedly connected to the limit screw 1510. The traction line 13 is vertically arranged to the tension test shaft 92 and the sliding optical axis 14. During the rotation of the sliding optical axis 14, the friction force generated by the shear stress of the lubricating oil on the journal surface of the sliding optical axis 14 causes the semi-floating ring bearing 1512 to generate a horizontal pulling force in the opposite direction that is balanced with the friction force. Since the semi-floating ring bearing 1512 fits tightly against the oil supply outer copper sleeve 156, the pulling force is transmitted to the oil supply outer copper sleeve 156, causing it to have a rotation tendency or rotation, and is transmitted to the tension sensor 9 via the traction line 13 wound around the limit screw 1510, and the tension sensor 9 can record the tension value.

[0024] like Figure 7-8As shown, the sliding optical axis support assembly 16 includes a sliding bearing base 161 fixedly connected to the stand base 1, a sliding bearing 162 for the sliding optical axis 14 to pass through is arranged in the sliding bearing base 161, an oil inlet hole is arranged above the sliding bearing base 161, and third transparent oil storage tanks 163 are correspondingly arranged at both ends of the sliding bearing 162, and an oil outlet hole is arranged at the lower end of the third transparent oil storage tank 163. The sliding optical axis support assembly 16 provides stable support for the sliding optical axis 14 during operation. A plurality of interconnected oil storage tanks 10 are arranged on the surface of the test bench base 1. A U-shaped oil storage tray 7 is 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 arranged on the front side of the oil storage tray 7, which is connected to an oil supply pump (not shown in the figure) through an oil delivery hose. The oil can be recycled through the oil supply pump, and the leaked oil generated during the test can be stored in the oil storage tank 10, which can not only improve the working environment at the work site, but also realize the recycling of oil.

[0025] A counterweight plate assembly 17 is correspondingly mounted on both ends of the sliding optical axis 14, and the counterweight plate assembly 17 includes a counterweight plate 171 which is slidably mounted on the sliding optical axis 14, and a wheel claw 172 mounted on the sliding optical axis 14 is fixedly connected to one side of the counterweight plate 171, and a locking sleeve 173 is threadedly connected to the end of the wheel claw 172 away from the counterweight plate 171, and the wheel claw 172 can be locked on the sliding optical axis 14 by rotating the locking sleeve 173 close to the counterweight plate 171; the position of the counterweight plate assembly 17 on the sliding optical axis 14 can be adjusted according to needs, and can be conveniently fixed; the counterweight plate assembly 17 provides counterweight for the sliding optical axis 14, thereby reducing the adverse effects of vibration on the detection results during the rotation of the sliding optical axis 14.

[0026] like Figures 1 to 3 and Fig.15As shown, the shaft system assembly 2 also includes a transmission pulley assembly 11 correspondingly arranged at one end of the sliding optical axis 14, and the transmission pulley assembly 11 includes two sets of rolling bearing bases 112 correspondingly arranged. The rolling bearing base 112 includes a base frame 1121 fixedly arranged on the platform base 1 and a rolling bearing 1122 installed in the base frame 1121. The inner rings of the two sets of rolling bearings 1122 are fixedly connected to the pulley shaft 111. One end of the pulley shaft 111 is fixedly connected to one end of the sliding optical axis 14 through a diaphragm coupling 12, and 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 arranged thereon. The power shaft end of the drive motor 5 is provided with a first synchronous pulley 8, and the first synchronous pulley 8 is connected to the second synchronous pulley 113 through a synchronous belt 3. The power drive mechanism 4 adopts a synchronous belt 3 and a transmission pulley assembly 11 to realize the rotational drive of the sliding optical axis 14; the power drive mechanism 4 and the shaft system assembly 2 are separated, which can reduce the influence of the vibration generated by the high-speed rotation of the drive motor 5 on the platform base 1, which is beneficial to improve the measurement accuracy of the dynamic friction coefficient.

[0027] The installation method of the measuring device 100 of the present invention comprises the following steps: (i) 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 bench base 1 accordingly.

[0028] (ii) Install the second synchronous pulley 113 in the center of the pulley shaft 111, and arrange the deep groove ball bearings 159 in the depressions 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, and it should be noted that the shaft end of the pulley shaft 111 is not easy to extend too long into the diaphragm coupling 12; the deep groove ball bearings 159 correspondingly connected at both ends of the pulley shaft 111 are respectively fixedly mounted in the base frame 1121, and the assembly of the transmission pulley assembly 11 is completed.

[0029] (3) Arrange the motor base 6 on the ground on one side of the gantry base 1, fix the drive motor 5 on the motor base 6, install the first synchronous pulley 8 on the motor shaft of the drive motor 5, and then connect the first synchronous pulley 8 to the second synchronous pulley 113 through the synchronous belt 3.

[0030] (IV) Install the pressure sensor 18 at the center of the bottom inner end of the bearing base outer frame 151, support the floating inner frame 152 on the pressure sensor 18, and fix the guide baffles 153 on the outer sides of the bearing base outer frame 151 by screws to limit the floating inner frame 152 in 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, and then install the oil supply outer copper sleeve retaining rings at both ends of the outer side of the oil supply outer copper sleeve 156, install the oil pipe joint 157 at one end of the oil supply outer copper sleeve 156, and install 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 a bearing retaining ring 1511 is placed in the inner groove of the oil supply outer copper sleeve 156 to fix the semi-floating ring bearing 1512 inside the oil supply outer copper sleeve 156, thereby completing the installation of the semi-floating ring bearing base assembly 15.

[0031] (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 depressions on both sides of the outer side of the sliding bearing base 161, and install the third transparent oil storage tank 163 on the outer sides of both ends of the sliding bearing base 161 to complete the sliding optical axis support assembly 16.

[0032] (VI) The tension sensor 9 is correspondingly arranged on the stand base 1 on one side of the semi-floating ring bearing base assembly 15, and one end of the traction line 13 is passed through the hole on the upper rear side of the second transparent oil storage tank 158 and fixedly connected to the limit screw 1510, and 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 storage tank 154 and the second transparent oil storage tank 158 are correspondingly fixedly connected to the outer sides of the two ends of the floating inner frame 152.

[0033] (VII) Assemble a set of counterweight plate assemblies 17 at one end of the sliding optical axis 14, then pass the other end of the sliding optical axis 14 through the axial holes provided in the center of the semi-floating ring bearing base assembly 15 and the sliding optical axis support assembly 16 in turn, install another set of mass plate assemblies on the sliding optical axis 14, and then fix the sliding optical axis 14 to the diaphragm coupling 12; the counterweight plate assembly 17 close to one end of the diaphragm coupling 12 does not come into contact with the diaphragm coupling 12, and the sliding optical axis 14 is not easy to extend too long into the diaphragm coupling 12.

[0034] (VIII) Move and adjust the two sets of counterweight plate assemblies 17 to appropriate positions on the sliding optical axis 14 respectively, and then fix the positions of the two sets of counterweight plate assemblies 17 by tightening the locking sleeve 173.

[0035] Embodiment 2: The present invention also discloses a method for measuring the coefficient of dynamic friction, the measuring method comprising: Step 1: After the measuring device 100 is assembled, it is installed on the ground in a specific area.

[0036] Step 2: Start the drive motor 5 according to the preset program, and the drive motor 5 drives the first synchronous pulley 8 to rotate by frequency conversion. The first synchronous pulley 8 drives the pulley shaft 111 to rotate through the synchronous belt 3 and the second synchronous pulley 113, and the pulley shaft 111 drives the sliding optical axis 14 to rotate synchronously through the diaphragm coupling 12; during the rotation of the sliding optical axis 14, the lubricating oil in the gap of the semi-floating ring bearing 1512 is driven to flow, and the lubricating oil generates an oil film force to balance the load force based on the dynamic pressure effect and lifts the journal of the sliding optical axis 14, so that the journal of the sliding optical axis 14 and the inner surface of the semi-floating ring bearing 1512 are separated from each other, so that the floating inner frame 152 fixing the semi-floating ring bearing 1512 moves up and down relatively along the bearing base outer frame 151. During this process, the pressure sensor 18 records the sum of the compressive load force and the gravity 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 axis 14.

[0037] Step 3: During the rotation of the sliding optical axis 14, the friction force generated by the shear stress of the lubricating oil on the journal surface of the sliding optical axis 14 causes the semi-floating ring bearing 1512 to generate a horizontal pulling force in the opposite direction that is balanced with the friction force. Since the semi-floating ring bearing 1512 fits tightly against the oil supply outer copper sleeve 156, the pulling force is transmitted to the oil supply outer copper sleeve 156, causing it to have a rotation tendency or rotation, and is transmitted to the tension sensor 9 via the traction line 13 wound around the limit screw 1510. The tension sensor 9 records the tension value in the process, that is, the dynamic friction force f.

[0038] Step 4: The dynamic friction coefficient μ can be obtained by using the friction coefficient calculation formula μ=f / W.

[0039] The above are preferred embodiments of the present invention. It should be pointed out that, for ordinary technicians in this technical field, several improvements and modifications can be made without departing from the principles of the present invention. These improvements and modifications should also be regarded as 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) comprises: A shaft system assembly (2), the shaft system assembly (2) comprising a sliding optical axis (14) and a semi-floating ring bearing base assembly (15) and a sliding optical axis support assembly (16) which are correspondingly sleeved on the sliding optical axis (14), the semi-floating ring bearing base assembly (15) and the sliding optical axis support assembly (16) being correspondingly fixedly supported on the platform base (1); A power drive mechanism (4), the power drive mechanism (4) being arranged correspondingly at one end of the shaft system component (2) and being transmission-connected to the sliding optical shaft (14) via a synchronous belt (3); A tension sensor (9) is correspondingly arranged at one end of the semi-floating ring bearing base assembly (15), and is transmission-connected to the semi-floating ring bearing base assembly (15) via a traction line (13), and is used to detect tangential tension during the rotation of the sliding optical axis (14).

2. The dynamic friction coefficient measuring device for a semi-floating ring bearing according to claim 1, characterized in that: The semi-floating ring bearing base assembly (15) comprises a bearing base outer frame (151) and a floating inner frame (152) vertically slidably connected inside the bearing base outer frame (151), wherein two ends of the floating inner frame (152) are respectively provided with a first transparent oil storage tank (154) and a second transparent oil storage tank (158); A pressure sensor (18) is provided at the bottom of the inner side of the bearing base outer frame (151) and is located below the floating inner frame (152), and guide baffles (153) are longitudinally provided on the outer sides of both sides of the bearing base outer frame (151), wherein the guide baffles (153) restrict the floating inner frame (152) inside the bearing base outer frame (151); A deep groove ball bearing (159) and an oil supply outer copper sleeve (156) sleeved on the inner ring of the deep groove ball bearing (159) are fixedly arranged in the floating inner frame (152); both ends of the oil supply outer copper sleeve (156) are sealed with oil supply outer copper sleeve retaining rings; an oil pipe joint (157) is arranged at one end of the oil supply outer copper sleeve (156), and a limiting screw (1510) is arranged at the top end of the other end of the oil supply outer copper sleeve (156); A semi-floating ring bearing (1512) is arranged in the oil supply outer copper sleeve (156) along its axial direction, and both ends of the semi-floating ring bearing (1512) are restricted in the oil supply outer copper sleeve (156) by bearing retaining rings (1511).

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

4. The dynamic friction coefficient measuring device for a semi-floating ring bearing according to claim 3, characterized in that: The tension sensor (9) comprises a first sensor base (91) and a tension test shaft (92) fixedly arranged at its upper end, the tension test shaft (92) being arranged in parallel with the sliding optical axis (14), and a connecting hole (93) being arranged at the front end of the tension test shaft (92), the connecting hole (93) being fixedly connected to one end of a traction line (13), the other end of the traction line (13) passing through a second transparent oil storage tank (158) and being fixedly connected to a limit screw (1510), the traction line (13) being arranged vertically to the tension test shaft (92) and the sliding optical axis (14).

5. The dynamic friction coefficient measuring device for a semi-floating ring bearing according to any one of claims 1 to 4, characterized in that: The sliding optical axis support assembly (16) comprises 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 arranged in the sliding bearing base (161), third transparent oil storage grooves (163) are arranged at both ends of the sliding bearing (162), and an oil outlet hole is arranged at the lower end of the third transparent oil storage groove (163).

6. The device for measuring the coefficient of dynamic friction of a semi-floating ring bearing according to claim 5, characterized in that: A plurality of interconnected oil storage tanks (10) are arranged on the surface of the platform base (1), and a U-shaped oil storage tray (7) is arranged on the platform 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).

7. The device for measuring the coefficient of dynamic friction of a semi-floating ring bearing according to claim 5, characterized in that: The two ends of the sliding optical axis (14) are correspondingly sleeved with a counterweight plate assembly (17), the counterweight plate assembly (17) comprising a counterweight plate (171) slidably sleeved on the sliding optical axis (14), one side of the counterweight plate (171) is fixedly connected to a wheel plate claw (172) sleeved on the sliding optical axis (14), one end of the wheel plate claw (172) away from the counterweight plate (171) is threadedly connected to a locking sleeve (173), and the wheel plate claw (172) can be locked on the sliding optical axis (14) by rotating the locking sleeve (173) close to the counterweight plate (171).

8. The device for measuring the coefficient of dynamic friction of a semi-floating ring bearing according to claim 7, characterized in that: The shaft system assembly (2) further comprises a transmission pulley assembly (11) correspondingly arranged at one end of the sliding optical axis (14); the transmission pulley assembly (11) comprises two sets of rolling bearing bases (112) correspondingly arranged; the rolling bearing base (112) comprises a base frame (1121) fixedly arranged on the platform base (1) and a rolling bearing (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 axis (14) via a diaphragm coupling (12); and a second synchronous pulley (113) is fixedly connected to the pulley shaft (111).

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

10. A method for measuring a coefficient of dynamic friction, characterized in that: Using the measuring device as claimed in claim 8, the measuring method comprises: Step 1: After the measuring device (100) is assembled, it is installed on the ground in a specific area; Step 2: The drive motor (5) is started according to a pre-set program. The drive motor (5) drives the first synchronous pulley (8) to rotate by frequency conversion. The first synchronous pulley (8) drives the pulley shaft (111) to rotate through the synchronous belt (3) and the second synchronous pulley (113). The pulley shaft (111) drives the sliding optical axis (14) to rotate synchronously through the diaphragm coupling (12). During the rotation of the sliding optical axis (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 journal of the sliding optical axis (14) is separated from the inner surface of the semi-floating ring bearing (1512), so that the floating inner frame (152) fixing the semi-floating ring bearing (1512) moves relatively up and down along the outer frame (151) of the bearing base. During this process, the pressure sensor (18) records the sum of the compressive load force and the gravity of the floating inner frame (152) and its internal components, and the radial load force W generated during the rotation of the sliding optical axis (14) is subtracted from the known weight of the floating inner frame (152) and its internal components. Step 3: During the rotation of the sliding optical axis (14), the friction force generated by the shear stress of the lubricating oil on the journal surface of the sliding optical axis (14) causes the semi-floating ring bearing (1512) to generate a horizontal pulling force in the opposite direction that is balanced with the friction force. Since the semi-floating ring bearing (1512) is tightly fitted with the oil supply outer copper sleeve (156), the pulling force is transmitted to the oil supply outer copper sleeve (156), causing it to have a rotation tendency or rotation, and is transmitted to the tension sensor (9) through the traction line (13) wound around the limit screw (1510). The tension sensor (9) records the tension value in the process, that is, the dynamic friction force f; Step 4: The dynamic friction coefficient μ can be obtained by using the friction coefficient calculation formula μ=f / W.

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