Device and method for measuring friction torque of rolling bearing under high speed and heavy load conditions

Abstract

The application discloses a kind of high speed and load working condition measured rolling bearing friction torque measuring device and method, the present application is by using pneumatic drive unit to generate high pressure gas blow rotary shaft high-speed rotation, simultaneously by rotary shaft drive measured rolling bearing's inner ring rotation, when rotary shaft speed specified speed, cut off gas source, measured rolling bearing's inner ring starts to decelerate under the action of friction torque;At this time, by collecting the deceleration acceleration of measured rolling bearing's inner ring, the bearing friction torque can be calculated.The present application adopts free deceleration method to measure rolling bearing friction torque, with simple device structure, lower installation requirement, can realize high speed and variable pre-tightening working condition measurement, and measurement precision is high, detection efficiency is high, and has the advantages such as practical value is high.

Description

Technical Field

[0001] This invention relates to the field of bearing measurement, and more particularly to a device and method for measuring the frictional torque of a rolling bearing under high-speed and load conditions. Background Technology

[0002] Frictional torque, a key indicator of bearing dynamic performance, directly affects the resistance, energy loss, temperature rise, and reliability of the bearing during operation. In terms of frictional torque measurement, only a few OEMs conduct tests when technical requirements dictate otherwise, and most measurements are only applicable to low-speed, static radial load conditions. Measurements of frictional torque under high-speed, dynamic axial load conditions (variable preload) are less common. Currently, domestic and international frictional torque measurement methods mainly include the balanced torque measurement method, the direct frictional torque measurement method, and the energy conversion method. These methods generally suffer from complex structures and high installation accuracy requirements.

[0003] The balanced torque measurement method is prone to introducing other interfering frictions, reducing measurement accuracy. Furthermore, regardless of whether a tension rope or spring is used, the frictional torque of the bearing being measured needs to overcome bending deformation to be transmitted to the tension sensor, which also affects measurement accuracy. The direct friction torque measurement method generally uses a torque sensor to directly measure mass friction torque; although it has high accuracy, it is expensive, easily damaged, and requires long auxiliary time, making it unsuitable for large-scale testing and high-speed measurements. Energy conversion methods, being indirect measurements, cannot guarantee measurement accuracy.

[0004] In summary, current testing devices are generally suitable for measurements under low-speed and static radial load conditions, but cannot measure bearing friction torque under high-speed and dynamic axial load (variable preload) conditions; existing measuring devices lack versatility and have low measurement accuracy; the auxiliary testing time of existing measuring devices is long and the testing efficiency is low, which cannot meet production needs. Summary of the Invention

[0005] The purpose of this invention is to provide a device and method for measuring the friction torque of a rolling bearing under high-speed and high-load conditions, so as to solve the problems of poor versatility and low measurement accuracy of existing rolling bearing friction torque measurement technologies.

[0006] To solve the above-mentioned technical problems, the present invention provides a measuring device for measuring the friction torque of a rolling bearing under high speed and load conditions, including a host computer, a lower support plate, an upper support plate, and a preload adjustment device that allows the upper support plate to move closer to or further away from the lower support plate with a single degree of freedom.

[0007] The lower support plate is provided with a mounting position that conforms to the outer ring of the rolling bearing being tested;

[0008] The upper support plate is equipped with a rotary drive device for driving the inner ring of the rolling bearing under test to rotate and a speed monitoring unit for monitoring the speed of the rotary drive device.

[0009] The rotary drive device includes a rotary shaft mounted on an upper support plate via an air bearing. The output end of the rotary shaft is detachably connected to the inner ring of the rolling bearing under test via a drive connector. The input end of the rotary shaft is connected to a pneumatic drive unit mounted on the upper support plate.

[0010] The host computer is connected to the speed monitoring unit to obtain the speed monitored by the speed monitoring unit and to calculate the friction torque of the rolling bearing under test based on the obtained speed.

[0011] Furthermore, the pneumatic drive unit includes a gear and a gear driver; the gear is fixedly connected to the input end of the rotating shaft, and the gear driver is mounted on the upper support plate via a gear support seat. The gear driver is provided with an air passage that is aligned with the teeth of the gear, and a high-pressure jet nozzle for injecting high-pressure gas into the gear to drive the rotating shaft to rotate is installed in the air passage.

[0012] Furthermore, the preload adjustment device includes a telescopic mechanism fixedly connected to the lower support plate and a connecting rod fixedly connected to the upper support plate. A tension / compression sensor is connected between the telescopic mechanism and the connecting rod. The telescopic device can be a guide rail cylinder, with the fixed end of the guide rail cylinder fixedly connected to the lower support plate and the movable end of the guide rail cylinder connected to the end of the tension / compression sensor away from the connecting rod.

[0013] Furthermore, the drive connector is a rubber head, one end of which is fixedly connected to the rotating shaft, and the other end of which is tapered.

[0014] Furthermore, the lower support plate is provided with a mounting groove, the outer ring of the rolling bearing under test is mounted on the groove wall of the mounting groove while keeping the inner ring of the rolling bearing under test suspended; the position in the mounting groove that is aligned with the rotating shaft is the mounting position.

[0015] Furthermore, each side wall of the mounting groove is provided with a step that conformally fits the outer ring of the rolling bearing under test, and the outer ring of the rolling bearing under test is mounted on the step.

[0016] Furthermore, the mounting slot extends through both ends of the lower support plate; the testing device also includes an automatic loading and unloading device for automatically sending the gear to be tested to the designated position of the mounting slot and for automatically unloading the gear to be tested that has been measured from the mounting position.

[0017] The automatic loading and unloading device includes a loading conveyor belt, a unloading conveyor belt, and an automatic pusher; the loading conveyor belt is located at the loading end of the mounting groove and is perpendicular to the mounting groove in the horizontal plane; the unloading conveyor belt is located at the unloading end of the mounting groove; the automatic pusher is installed on the side of the loading conveyor belt away from the mounting groove and is aligned with the mounting groove.

[0018] Furthermore, guide rails are provided at both ends of the lower support plate, and sliding holes that mate with the guide rails are provided on the upper support plate. The upper support plate moves along the guide rails under the action of the preload adjustment device. Sleeves that mate with the guide rails can also be installed in the sliding holes of the upper support plate.

[0019] This invention also provides a method for measuring the frictional torque of a rolling bearing under test. This method is based on the aforementioned device for measuring the frictional torque of a rolling bearing under high-speed and load conditions. The method includes:

[0020] Connect the rotating shaft to the inner ring of the rolling bearing being tested, and adjust the distance between the lower support plate and the upper support plate by adjusting the preload adjustment device to set the preload between the rotating shaft and the rolling bearing being tested;

[0021] The pneumatic drive unit drives the rotary drive device to rotate, and at the same time, the speed monitoring unit is activated to monitor the speed of the rotary drive device in real time. When the speed of the rotary drive device reaches the specified value, the pneumatic power input is stopped.

[0022] The rotational speed of the rotary drive device is monitored in real time by the host computer using the rotational speed monitoring unit. The deceleration acceleration of the rotary drive device after the pneumatic power input stops is calculated based on the rotational speed. Then, the frictional torque of the tested rolling bearing is calculated based on the deceleration acceleration.

[0023] The beneficial effects of this invention are as follows:

[0024] 1. A pneumatic drive unit generates high-pressure air to propel a rotating shaft at high speed. Simultaneously, the rotating shaft drives the inner ring of the rolling bearing under test to rotate. When the rotating shaft reaches a specified speed, the air supply is cut off, and the inner ring of the rolling bearing begins to decelerate under the action of frictional torque. At this point, by collecting the deceleration acceleration of the inner ring of the rolling bearing under test, the bearing frictional torque can be calculated. This application uses the free deceleration method to measure the frictional torque of rolling bearings. It has advantages such as simple device structure, low installation requirements, ability to achieve high-speed and variable preload conditions, high measurement accuracy, high detection efficiency, and high practical value.

[0025] 2. By adopting pneumatic drive and mounting the rotating shaft on the upper support plate through air bearings, the resistance of the rotating shaft is small, and high-speed rotation can be achieved under the action of high-pressure air; and there are no other sources of frictional torque except for the rolling bearing being measured, which can eliminate frictional interference to the greatest extent and create a frictionless environment to improve the measurement accuracy of bearing frictional torque.

[0026] 3. The preload adjustment device allows the upper support plate to move closer to or further away from the lower support plate with a single degree of freedom, thereby driving the rotating shaft mounted on the upper support plate to move and adjust the preload between the rotating shaft and the rolling bearing being measured, thus realizing the measurement of bearing friction under variable preload conditions.

[0027] 4. By setting an electromagnetic damper, when the rotational speed of the tested rolling bearing decreases to a level sufficient for calculating deceleration under the action of frictional torque, the electromagnetic damper can quickly stop the rotating shaft from rotating, thereby improving the detection efficiency.

[0028] 5. By setting up an automatic loading and unloading device, it is possible to realize the automatic feeding, testing, and unloading processes of the rolling bearings under test, thereby improving testing efficiency. Attached Figure Description

[0029] The accompanying drawings, which are included to provide a further understanding of this application and form part of this application, use the same reference numerals to denote the same or similar parts. The illustrative embodiments of this application and their descriptions are used to explain this application and do not constitute an undue limitation of this application. In the drawings:

[0030] Figure 1 This is a perspective view of an embodiment of the present invention;

[0031] Figure 2 This is a partial cross-sectional view of an embodiment of the present invention;

[0032] Figure 3 This is a partial cross-sectional view of a pneumatic drive unit according to an embodiment of the present invention;

[0033] Figure 4 This is an experimental data analysis diagram of one embodiment of the present invention.

[0034] The components are as follows: 1. Lower support plate; 11. Bearing mounting position to be tested; 2. Upper support plate; 21. Groove; 22. Air bearing; 3. Guide rail; 31. Fixed seat; 32. Sliding sleeve; 33. Anti-detachment component; 4. Rotating shaft; 41. Gear; 42. Gear driver; 421. Air passage; 422. High-pressure jet nozzle; 43. Gear support seat; 44. Damper; 5. Rubber head; 51. Cone; 6. Rolling bearing to be tested; 7. Guide rail cylinder; 71. Tension / compression sensor; 72. Connecting rod; 73. Nut; 8. Encoder; 9. Feeding conveyor belt; 91. Feeding cylinder; 92. Unloading conveyor belt. Detailed Implementation

[0035] like Figure 1 and Figure 2The high-speed, high-load rolling bearing friction torque measuring device shown includes a host computer, a lower support plate 1, an upper support plate 2, and a preload adjustment device that allows the upper support plate 2 to move closer to or further away from the lower support plate 1 with a single degree of freedom. The lower support plate 1 has a mounting position 11 that conformally fits the outer ring of the rolling bearing 6 under test. The upper support plate 2 has a rotary drive device for driving the inner ring of the rolling bearing 6 under test to rotate and a speed monitoring unit for monitoring the speed of the rotary drive device. The rotary drive device includes a rotary shaft 4 mounted on the upper support plate 2 via an air bearing 22. The output end of the rotary shaft 4 is detachably connected to the inner ring of the rolling bearing 6 under test via a drive connector, and the input end of the rotary shaft 4 is connected to a pneumatic drive unit mounted on the upper support plate 2. The host computer is signal-connected to the speed monitoring unit to acquire the speed monitored by the speed monitoring unit and calculate the friction torque of the rolling bearing under test based on the acquired speed.

[0036] This application utilizes a pneumatic drive unit to generate high-pressure air, propelling a rotating shaft 4 to rotate at high speed. Simultaneously, the rotating shaft 4 drives the inner ring of the tested rolling bearing 6 to rotate. When the rotating shaft 4 reaches a specified speed, the air supply is cut off, and the inner ring of the tested rolling bearing 6 begins to decelerate under the action of frictional torque. At this point, the speed monitoring unit collects the speed of the inner ring of the tested rolling bearing 6 and calculates the deceleration acceleration, thereby calculating the bearing frictional torque. This application uses the free deceleration method to measure the frictional torque of rolling bearings, which has advantages such as simple device structure, low installation requirements, ability to achieve high-speed and variable preload conditions, high measurement accuracy, and high practical value. The speed monitoring unit can be an encoder; by collecting the speed of the gears through the encoder, the speed of the rotating shaft rotating synchronously with the gears and the speed of the inner ring of the tested rolling bearing 6 can be obtained.

[0037] According to one embodiment of this application, such as Figure 3As shown, the pneumatic drive unit includes a gear 41 and a gear driver 42. The gear 41 is fixedly connected to the input end of the rotating shaft 4. The gear driver 42 is mounted on the upper support plate 2 via a gear support base 43. The gear driver 42 has an air passage 421 aligned with the teeth of the gear 41. A high-pressure jet nozzle 422 is installed in the air passage 421 to inject high-pressure gas into the gear 41 to drive the rotating shaft 4 to rotate. The high-pressure jet nozzle 422 is connected to an air source. To improve the driving force and ensure the balance of the gear 41, gear drivers 42 can be symmetrically or evenly distributed around the gear 41. During measurement, multiple gear drivers 42 are activated simultaneously to drive the gear 41 to rotate. The gear 41 drives the rotating shaft 4 to rotate, and simultaneously drives the inner ring of the rolling bearing 6 being measured to rotate. This embodiment, by adopting a pneumatic drive method, is easy to control and does not introduce other frictional torques. The gear driver 42 has an arc-shaped groove on the side facing the gear 41 that conforms to the gear 41. The side of the gear driver 42 facing the gear 41 is an arc-shaped surface. The exhaust port of the air passage 421 is located at the maximum concavity of the arc-shaped groove, and the outermost side of the high-pressure airflow direction in the exhaust port is tangent to the tooth tip circle of the gear 41, which can ensure the driving force of the high-pressure airflow.

[0038] According to one embodiment of this application, the air bearing 22 can be an existing air static pressure bearing. The rotating shaft 4 is fixed inside the inner ring of the air static pressure bearing, and the outer ring of the air static pressure bearing is provided with a flange-type mounting seat. The air static pressure bearing is fixed to the upper support plate 2 through the flange-type mounting seat. The upper support plate 2 is provided with a groove 21 adapted to the end of the air static pressure bearing to facilitate the installation of the air static pressure bearing. This application uses pneumatic drive and mounts the rotating shaft 4 on the upper support plate 2 through the air bearing 22. The resistance of the rotating shaft 4 is small, and high-speed rotation can be achieved under the action of high-pressure air. Furthermore, apart from the rolling bearing 6 being measured, there are no other sources of frictional torque, which can eliminate friction interference to the greatest extent and create a frictionless environment to improve the measurement accuracy of bearing frictional torque.

[0039] According to one embodiment of this application, the preload adjustment device includes a telescopic mechanism fixedly connected to the lower support plate 1 and a connecting rod 72 fixedly connected to the upper support plate 2. A tension / compression sensor 71 is connected between the telescopic mechanism and the connecting rod 72. The preload adjustment device allows the upper support plate 2 to move closer to or further away from the lower support plate 1 with a single degree of freedom, thereby moving the rotating shaft 4 mounted on the upper support plate 2 to adjust the preload between the rotating shaft 4 and the rolling bearing 6 being measured, thus achieving the measurement of bearing friction under variable preload conditions. The telescopic device can be a guide rail cylinder 7, with its fixed end fixedly connected to the lower support plate 1 and its movable end connected to the end of the tension / compression sensor 71 away from the connecting rod 72. The connecting rod 72 is threadedly connected to the upper support plate 2 and locked with a nut.

[0040] According to one embodiment of this application, the upper support plate 2 is provided with an electromagnetic damper 44 for stopping the rotation of the rotating shaft 4. When the bearing speed decreases to a level sufficient for calculating deceleration under the action of frictional torque, the electromagnetic damper 44 can quickly stop the rotation of the rotating shaft 4, thereby improving detection efficiency.

[0041] According to one embodiment of this application, the drive connector is a rubber head 5. One end of the rubber head 5 is fixedly connected to the rotating shaft 4, and the other end of the rubber head 5 is tapered. The rubber head 5 is made of elastic material. The end of the rubber head 5 connected to the rotating shaft 4 has a connecting groove that mates with the rotating shaft 4, and the rotating shaft 4 is fixed in the connecting groove. The maximum diameter of the rubber head 5 is larger than the diameter of the inner ring of the rolling bearing 6 being tested. When the rotating shaft 4 moves closer to or further away from the lower support plate 1 with the upper support plate 2 under the action of the preload adjustment device, the rubber head 5 at the output end of the rotating shaft 4 contacts and separates from the inner ring of the rolling bearing 6 being tested. When the rubber head 5 contacts the inner ring of the rolling bearing 6 being tested, the contact force between the rubber head 5 and the rolling bearing 6 being tested can be adjusted by adjusting the pressure of the guide cylinder 7 through the electromagnetic proportional valve, thereby realizing the measurement of the friction torque of the rolling bearing 6 being tested under variable preload conditions. The magnitude of the loading force is measured by a tension / compression sensor 71 installed between the telescopic mechanism and the connecting rod 72, which can realize quantitative loading.

[0042] According to one embodiment of this application, the lower support plate 1 is provided with a mounting groove. The outer ring of the rolling bearing 6 to be tested is mounted on the groove wall of the mounting groove while keeping the inner ring of the rolling bearing 6 suspended. The position in the mounting groove aligned with the rotating shaft 4 is the mounting position 11. The contact surface between the groove wall of the mounting groove and the outer ring of the rolling bearing is a non-smooth surface. When the rotation drive device drives the inner ring of the rolling bearing 6 to rotate, since the friction between the inner and outer rings of the rolling bearing 6 is much smaller than the friction between the outer ring of the rolling bearing and the mounting seat, it is not necessary to fix the outer ring of the rolling bearing. This installation method has a simple structure, low installation requirements, and is easy to implement and promote.

[0043] According to one embodiment of this application, each side wall of the mounting groove is provided with a step that conformally fits the outer ring of the rolling bearing 6 to be measured. During measurement, the outer ring of the rolling bearing 6 to be measured is mounted on the step. In order to increase the friction between the outer ring of the rolling bearing 6 to be measured and the step to a certain extent, the surface of the step can be roughened, or a rubber pad to increase the friction can be provided on the step.

[0044] According to one embodiment of this application, the mounting groove extends through both ends of the lower support plate 1; the detection device also includes an automatic loading and unloading device for automatically sending the gear 41 to be tested to a designated position in the mounting groove and for automatically unloading the gear 41 to be tested after measurement from the mounting position 11; by setting the automatic loading and unloading device, it is beneficial to realize the automatic feeding, detection, and unloading processes of the rolling bearing 6 to be tested, thereby improving the detection efficiency.

[0045] The automatic loading and unloading device includes a loading conveyor belt 9, an unloading conveyor belt 92, and an automatic pusher. The loading conveyor belt 9 is located at the loading end of the mounting slot and is perpendicular to the mounting slot in the horizontal plane. The unloading conveyor belt 92 is located at the unloading end of the mounting slot. The automatic pusher is installed on the side of the loading conveyor belt 9 away from the mounting slot and is aligned with the mounting slot. The automatic pusher can be a cylinder. The loading conveyor belt 9 transports the rolling bearing 6 to be tested to the designated position aligned with the mounting slot. Then, the feed cylinder 91 pushes the rolling bearing 6 to be tested to the mounting position 11. After the test is completed, the feed cylinder 91 pushes the rolling bearing 6 to be tested onto the unloading conveyor belt 92, which then transports the rolling bearing 6 to the next testing process.

[0046] According to one embodiment of this application, guide rails 3 are respectively provided at both ends of the lower support plate 1, and sliding holes that cooperate with the guide rails 3 are provided on the upper support plate 2. The upper support plate 2 moves along the guide rails 3 under the action of the preload adjustment device. A sliding sleeve 32 that cooperates with the guide rails 3 can also be provided in the sliding holes of the upper support plate 2 to reduce friction. Sliding friction is formed between the guide rails 3 and the upper support plate 2, providing stable guidance and load-bearing function for the up and down movement of the upper support plate 2. The lower support plate 1 provides stable support for the entire detection device, and the guide rails 3 are mounted on the lower support plate 1 through the fixing seat 31. The guide rails 3 are cylindrical to avoid stress concentration. An anti-detachment component 33 is provided at the top of the guide rails 3 to limit the sliding stroke of the upper support plate 2.

[0047] This invention also provides a method for measuring the frictional torque of a rolling bearing under test. This method is based on the aforementioned device for measuring the frictional torque of a rolling bearing under high-speed and load conditions. The method includes:

[0048] Connect the rotating shaft 4 to the inner ring of the rolling bearing 6 being tested, and adjust the distance between the lower support plate 1 and the upper support plate 2 through the preload adjustment device to set the preload between the rotating shaft 4 and the rolling bearing 6 being tested;

[0049] The pneumatic drive unit drives the rotary drive device to rotate, and at the same time, the speed monitoring unit is activated to monitor the speed of the rotary drive device in real time. When the speed of the rotary drive device reaches the specified value, the pneumatic power input is stopped, and the speed n of the rotary drive device monitored in real time by the speed monitoring unit is obtained.

[0050] The rotational speed n of the rotary drive device is monitored in real time by the host computer using the speed monitoring unit. The deceleration acceleration of the rotary drive device after the pneumatic power input stops is calculated based on the rotational speed n. Then, the frictional torque M of the tested rolling bearing is calculated based on the deceleration acceleration.

[0051] Data analysis method for measuring bearing friction torque using the free deceleration method: During the experiment, the rotating shaft 47 is propelled by high-pressure air to 1.1 times the experimental speed, then the high-pressure air is turned off, allowing the rotating shaft 47 to decelerate freely under the action of the friction torque of the bearing being tested. The power loss of the bearing being tested is:

[0052]

[0053] In the formula, J represents the moment of inertia of the rotating shaft 4 and its associated rotating parts. The rotating shaft 4 and its associated rotating parts are made of different materials and have irregular structures, with some overlap between them. Therefore, their moment of inertia is difficult to calculate accurately theoretically. Experimental measurement of their moment of inertia is a simple, accurate, and effective method. This experiment uses the auxiliary pendulum method to measure the moment of inertia of the rotating shaft 4 and its associated rotating parts. M represents the frictional torque, and ω represents the angular velocity. dn / dt represents the deceleration acceleration during free deceleration at a rotational speed of n. Polynomial regression analysis is used to denoise and smooth the data to reduce errors. The curve fitting tool (Cftool) in Matlab software is used to perform polynomial fitting on the experimental data. By differentiating the fitting result, the deceleration acceleration dn / dt can be obtained.

[0054] Taking an experimental rotational speed n of 24000 r / min as an example, the experimental results are as follows: Figure 4 As shown. The coordinates corresponding to the rotational speed n of the rotating shaft 4 at 24000 r / min are (t0, n0), and the fitted curve p(t) is basically consistent with the experimental curve n(t). Figure 4 The slope p'(t0) of the tangent y is the deceleration acceleration obtained by differentiating the fitted curve p(t), that is, the acceleration dn / dt during deceleration is equal to p'(t0). Finally, the friction torque M of the tested bearing is obtained as -p'(t0)·J.

[0055] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention and are not intended to limit it. Although the present invention has been described in detail with reference to preferred embodiments, those skilled in the art should understand that modifications or equivalent substitutions can be made to the technical solutions of the present invention without departing from the spirit and scope of the technical solutions of the present invention, and all such modifications or substitutions should be covered within the scope of the claims of the present invention.

Claims

1. A device for measuring the frictional torque of a rolling bearing under high-speed and loaded conditions, characterized in that, It includes a host computer, a lower support plate, an upper support plate, and a preload adjustment device that allows the upper support plate to move closer to or further away from the lower support plate with a single degree of freedom; The lower support plate is provided with a mounting position that conforms to the outer ring of the rolling bearing being tested; The upper support plate is provided with a rotary drive device for driving the inner ring of the tested rolling bearing to rotate and a speed monitoring unit for monitoring the speed of the rotary drive device. The rotary drive device includes a rotary shaft mounted on an upper support plate via an air bearing. The output end of the rotary shaft is detachably connected to the inner ring of the rolling bearing under test via a drive connector, and the input end of the rotary shaft is connected to a pneumatic drive unit mounted on the upper support plate. The host computer is connected to the speed monitoring unit to obtain the speed monitored by the speed monitoring unit, calculate the deceleration acceleration of the rotary drive device after the pneumatic power input stops based on the speed, and then calculate the friction torque of the tested rolling bearing based on the deceleration acceleration.

2. The measuring device for measuring the frictional torque of a rolling bearing under high-speed and loaded conditions according to claim 1, characterized in that, The pneumatic drive unit includes a gear and a gear driver; the gear is fixedly connected to the input end of the rotating shaft, and the gear driver is mounted on the upper support plate through a gear support seat. The gear driver is provided with an air passage that is aligned with the teeth of the gear, and a high-pressure jet nozzle for injecting high-pressure gas into the gear to drive the rotating shaft to rotate is installed in the air passage.

3. The measuring device for measuring the friction torque of a rolling bearing under high-speed and loaded conditions according to claim 1, characterized in that, The preload adjustment device includes a telescopic mechanism fixedly connected to the lower support plate and a connecting rod fixedly connected to the upper support plate. A tension / compression sensor is connected between the telescopic mechanism and the connecting rod.

4. The measuring device for measuring the friction torque of a rolling bearing under high-speed and loaded conditions according to claim 1, characterized in that, The drive connector is a rubber head, one end of which is fixedly connected to the rotating shaft, and the other end of which is tapered.

5. The measuring device for measuring the friction torque of a rolling bearing under high-speed and loaded conditions according to claim 1, characterized in that, The upper support plate is equipped with an electromagnetic damper for stopping the rotation of the rotating shaft.

6. The measuring device for measuring the frictional torque of a rolling bearing under high-speed and loaded conditions according to claim 1, characterized in that, The lower support plate is provided with a mounting groove, and the outer ring of the rolling bearing under test is mounted on the groove wall of the mounting groove while keeping the inner ring of the rolling bearing under test suspended; the position in the mounting groove that is aligned with the rotating shaft is the mounting position.

7. The measuring device for measuring the frictional torque of a rolling bearing under high-speed and loaded conditions according to claim 6, characterized in that, The mounting groove has a step on each of its two side walls that conforms to the outer ring of the rolling bearing under test, and the outer ring of the rolling bearing under test is mounted on the step.

8. The measuring device for measuring the frictional torque of a rolling bearing under high-speed and loaded conditions according to claim 6, characterized in that, The mounting groove extends through both ends of the lower support plate; the measuring device also includes an automatic loading and unloading device for automatically sending the gear to be measured to the designated position of the mounting groove and for automatically unloading the gear to be measured from the mounting position after measurement. The automatic loading and unloading device includes a loading conveyor belt, a unloading conveyor belt, and an automatic pusher; the loading conveyor belt is located at the loading end of the mounting groove and is perpendicular to the mounting groove in the horizontal plane; the unloading conveyor belt is located at the unloading end of the mounting groove; the automatic pusher is installed on the side of the loading conveyor belt away from the mounting groove and is aligned with the mounting groove.

9. The measuring device for measuring the frictional torque of a rolling bearing under high-speed and loaded conditions according to claim 1, characterized in that, The lower support plate is provided with guide rails at both ends, and the upper support plate is provided with sliding holes that cooperate with the guide rails. The upper support plate moves along the guide rails under the action of the preload adjustment device.

10. A method for measuring the frictional torque of a rolling bearing under test, characterized in that, This method is based on the high-speed and loaded rolling bearing friction torque measuring device described in any one of claims 1-9, and the method includes: Connect the rotating shaft to the inner ring of the rolling bearing being tested, and adjust the distance between the lower support plate and the upper support plate by adjusting the preload adjustment device to set the preload between the rotating shaft and the rolling bearing being tested; The pneumatic drive unit drives the rotary drive device to rotate, and at the same time, the speed monitoring unit is activated to monitor the speed of the rotary drive device in real time. When the speed of the rotary drive device reaches the specified value, the pneumatic power input is stopped. The rotational speed of the rotary drive device is monitored in real time by the host computer using the rotational speed monitoring unit. The deceleration acceleration of the rotary drive device after the pneumatic power input stops is calculated based on the rotational speed. Then, the frictional torque of the tested rolling bearing is calculated based on the deceleration acceleration.

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