One-way clutch bearing tester

Abstract

The utility model discloses a one -way clutch bearing testing machine, including frock table, hydraulic brake structure, clutch structure, main shaft, mandrel and oil tank, the mandrel end is inserted into the oil tank and the mandrel end detachable connection has the one -way clutch bearing of waiting test, the mandrel beginning and main shaft are through clutch structure linkage cooperation arrangement, the mandrel and hydraulic brake structure linkage cooperation and provide reverse torque to mandrel through hydraulic brake structure to simulate the brake working condition when bearing actual operation, be provided with the torque loading structure for applying torque to mandrel to simulate the torque working condition of bearing braking on frock table, be provided with the drive structure for driving main shaft high -speed operation to simulate the empty load rotation working condition when car actual operation on frock table. Solveed the problem that traditional one -way clutch bearing testing machine detects single -function, is difficult to simulate the actual operation working condition of bearing, the control working condition of sudden change and stress working condition.

Description

Technical Field

[0001] This utility model relates to the technical field of one-way clutch bearing testing equipment, specifically a one-way clutch bearing testing machine. Background Technology

[0002] One-way clutch bearings, as sliding bearings that can only rotate in one direction and will jam if reversed, require durability tests that meet requirements such as rapid speed changes, torque loading, and oil bath temperature control. However, existing one-way clutch bearing testing machines have shortcomings in rapid speed change control, torque loading accuracy, oil temperature control reliability, and system coordination, making it difficult to accurately verify the durability of this type of bearing. In addition, traditional one-way clutch bearing testing machines have limited testing functions and cannot simulate the actual operating conditions of the bearing. Utility Model Content

[0003] To address the shortcomings of existing technologies, this utility model provides a one-way clutch bearing testing machine, which solves the problems of traditional one-way clutch bearing testing machines having limited testing functions and difficulty in simulating actual bearing operating conditions, rapid speed change control conditions, and stress conditions.

[0004] To achieve the above objectives, this utility model provides a one-way clutch bearing testing machine, including a tooling table, a hydraulic brake structure, a clutch structure, a main shaft, a mandrel, and an oil tank. The end of the mandrel is placed in the oil tank, and the end of the mandrel is detachably connected to the one-way clutch bearing to be tested. The beginning of the mandrel is linked to the main shaft through the clutch structure. The mandrel is linked to the hydraulic brake structure, and the hydraulic brake structure provides a reverse torque to the mandrel to simulate the braking condition of the bearing during actual operation. The tooling table is provided with a torque loading structure for applying torque to the mandrel to simulate the torque condition of the bearing during braking. The tooling table is also provided with a drive structure for driving the main shaft to rotate at high speed to simulate the no-load rotation condition of a car during actual operation.

[0005] The advantages of adopting the above technical solution are: The technology integrates various functional modules through a tooling table, enabling the mandrel and spindle to be linked via a clutch. The hydraulic braking system provides a reverse torque when the bearing under test is running, and a torque loading structure simulates braking torque. The drive structure achieves high-speed, no-load rotation of the mandrel, forming a complete testing system. Through the coordinated design of these structures, the system simulates the bearing's actual operating conditions, such as rapid speed changes and torque loading, thus reproducing the bearing's actual operating scenario and ensuring the accuracy and reliability of durability performance testing. Furthermore, the system has a compact layout and is easy to maintain.

[0006] The present invention further includes the following: the hydraulic brake structure includes a brake disc and a brake caliper for working in conjunction with the brake disc to achieve brake closure or disengagement, wherein the brake disc is coaxially connected to the spindle.

[0007] The advantages of adopting the above technical solution are: in the hydraulic brake structure, the brake disc and spindle are coaxially connected, and the brake caliper is linked to the brake disc to achieve closure or disengagement, which can precisely control the timing and force of braking. The coaxial design of the brake disc and spindle ensures stable transmission of reverse torque, avoids the impact of off-center load on test accuracy, and can effectively simulate the actual braking conditions of the bearing. At the same time, the hydraulically driven brake caliper responds quickly and works with the brake disc to provide stable braking force, making the torque loading in the test more consistent with the real operating state and improving the validity of the test data.

[0008] The present invention further includes the following configuration: the clutch structure includes a pneumatic clutch, wherein the spindle and the main shaft are coaxially and linkedly configured via the pneumatic clutch to achieve closed connection or disconnection of the spindle and the main shaft via the pneumatic clutch.

[0009] The advantages of adopting the above technical solution are: the above technology uses a pneumatic clutch to connect the spindle and the main shaft, and the two can be quickly closed or opened through pneumatic control. When the drive structure starts and drives the main shaft to rotate at high speed, the pneumatic clutch closes and drives the spindle to rotate at high speed; while when braking, the clutch is opened to ensure power separation when the servo motor applies reverse torque, accurately simulating the rapid speed change condition.

[0010] The present invention further includes the following: the torque loading structure includes a servo motor, a drive shaft, a diaphragm coupling and a reducer. The servo motor is mounted on a tooling table and is linked with the drive shaft through the reducer and the diaphragm coupling. The end of the drive shaft is placed in an oil tank and is detachably connected to and coaxially arranged with the spindle.

[0011] The advantages of adopting the above technical solution are as follows: In the above technology, the torque loading structure drives the transmission shaft through a servo motor, a reducer, and a diaphragm coupling, so that the drive shaft and the spindle are coaxially connected. The servo motor and the reducer provide a stable torque output, while the diaphragm coupling compensates for coaxiality errors and ensures smooth torque transmission. Through the above design, the torque conditions experienced by the bearing during braking can be accurately simulated. The high-precision control of the servo motor makes the torque loading more in line with actual needs, improving the accuracy and reliability of torque simulation in the experiment.

[0012] The present invention further includes a torque sensor in the torque loading structure, which is configured to work in conjunction with the drive shaft.

[0013] The advantages of adopting the above technical solution are as follows: The torque sensor installed in the torque loading structure can monitor the torque value transmitted by the drive shaft in real time and feed the data back to an external control system or intelligent industrial control equipment. The external control system or intelligent industrial control equipment then adjusts the hydraulic pressure of the hydraulic brake caliper based on the torque value output by the torque sensor, achieving dynamic and precise torque adjustment. This avoids torque fluctuations affecting the test results. The above design ensures the stability and accuracy of torque loading, making the test data more realistically reflect the bearing's performance under actual working conditions and improving test accuracy.

[0014] The present invention further includes the following configuration: the drive structure includes a variable frequency motor mounted on a tooling table, and the variable frequency motor is connected to the main shaft by a synchronous belt drive.

[0015] The advantages of adopting the above technical solution are: the drive structure uses a variable frequency motor to drive the main shaft through a synchronous belt. The variable frequency motor can precisely adjust the speed to simulate the high-speed no-load rotation of the main shaft. The synchronous belt drive has the characteristics of smooth transmission, low noise, and convenient maintenance, which can ensure the stability of the main shaft rotation and reduce the impact of vibration on the test. Through the above design, the testing machine can accurately simulate the no-load rotation condition of the car in actual operation, providing reliable working conditions for bearing durability testing.

[0016] The present invention further includes the following features: the oil tank is filled with lubricating oil, the one-way clutch bearing to be tested is immersed in the lubricating oil, the oil tank is equipped with a temperature control structure for detecting the temperature of the lubricating oil, and the oil tank is equipped with a liquid level switch.

[0017] The advantages of adopting the above technical solution are: in the above technology, the lubricating oil in the oil tank immerses the bearing to be tested, which plays a role in lubrication and cooling, while the temperature control structure controls the oil temperature, and the liquid level switch prevents dry burning. The above technology simulates the actual lubrication state of the bearing by the lubricating oil environment, and the temperature control structure ensures the stability of the oil temperature, avoiding the impact of temperature fluctuations on the bearing performance test. The liquid level switch monitors the oil level in real time, and when the oil level is insufficient, it triggers protection to prevent the equipment from dry burning and damage, ensuring that the test is carried out safely and reliably.

[0018] The present invention further includes: the temperature control structure comprising an electric heating element installed on the oil tank, a temperature sensor for detecting the temperature of the lubricating oil inside the oil tank, and a temperature controller for working in conjunction with the electric heating element to control the temperature of the lubricating oil.

[0019] The advantages of adopting the above technical solution are: the interconnected design of the heating element, temperature sensor, and temperature controller in the temperature control structure allows for real-time detection of the lubricating oil temperature by the temperature sensor, and the temperature controller controls the heating element based on the oil temperature data fed back by the temperature sensor. This design achieves precise adjustment and stable control of the lubricating oil temperature, keeping it within the required range for the test and preventing abnormal temperatures from affecting the bearing test results. Attached Figure Description

[0020] Figure 1 This is a three-dimensional view of the present invention;

[0021] Figure 2 for Figure 1 A 3D view after hiding parts of the structure. Detailed Implementation

[0022] This utility model provides a one-way clutch bearing testing machine, including a tooling table 1, a hydraulic brake structure, a clutch structure, a main shaft 2, a mandrel 3, and an oil tank 11. The end of the mandrel 3 is inserted into the oil tank 11, and the end of the mandrel 3 is detachably connected to the one-way clutch bearing 31 to be tested. The beginning of the mandrel 3 is linked to the main shaft 2 through the clutch structure. The mandrel 3 is linked to the hydraulic brake structure, and the hydraulic brake structure provides a reverse torque to the mandrel 3 to simulate the braking condition of the bearing during actual operation. The tooling table 1 is provided with a tool for applying torque to the mandrel 3. A torque loading structure is provided to apply torque to simulate the torque conditions experienced by a bearing during braking. The tooling table 1 is equipped with a drive structure for driving the main shaft 2 at high speed to simulate the no-load rotation conditions during actual vehicle operation. The hydraulic braking structure includes a brake disc 4 and a brake caliper 41 that engages with the brake disc 4 to achieve brake closure or disengagement. The brake disc 4 is coaxially connected to the spindle 3. The clutch structure includes a pneumatic clutch 21, through which the spindle 3 and the main shaft 2 are coaxially connected and engaged. To achieve closed or open connection between the mandrel 3 and the main shaft 2, the torque loading structure includes a servo motor 5, a drive shaft 51, a diaphragm coupling 52, and a reducer 53. The servo motor 5 is mounted on the tooling table 1 and is linked to the drive shaft 51 via the reducer 53 and the diaphragm coupling 52. The end of the drive shaft 51 is inserted into the oil tank 11 and is detachably connected to the mandrel 3 and coaxially arranged. The torque loading structure also includes a torque sensor 54, which is linked to the drive shaft 51. The drive structure includes components mounted on the tooling table. The variable frequency motor 12 on the main shaft 2 is connected to the main shaft 2 by a synchronous belt 121. The oil tank 11 is filled with lubricating oil. The one-way clutch bearing 31 to be tested is immersed in the lubricating oil. The oil tank 11 is equipped with a temperature control structure for detecting the temperature of the lubricating oil. The oil tank 11 is equipped with a liquid level switch 111. The temperature control structure includes an electric heating tube 112 installed on the oil tank 11, a temperature sensor for detecting the temperature of the lubricating oil inside the oil tank 11, and a temperature controller for linkage with the electric heating tube 112 to control the temperature of the lubricating oil.

[0023] The operation process of the above technology is as follows:

[0024] First, the variable frequency motor is started. At this time, the pneumatic clutch is in the closed state, while the brake caliper is in the open state. The variable frequency motor drives the spindle to rotate at high speed through the drive spindle, thus simulating the no-load rotation condition of a car. Then, the pneumatic clutch disengages, the brake caliper closes, and the servo motor rotates in the opposite direction through the reducer and drive shaft, applying a reverse torque to the spindle through the hydraulic braking structure. At the same time, the torque sensor monitors the torque in real time and performs closed-loop control to simulate the torque condition of bearing braking. Subsequently, the servo motor stops, the brake caliper releases, and the pneumatic clutch closes again, returning to the high-speed no-load rotation state. This cycle repeats. During this period, the temperature control structure in the oil tank maintains a stable lubricating oil temperature through electric heating tubes and water coolers, and the level switch monitors the oil level in real time to prevent dry burning, ensuring that the test can be carried out continuously and reliably.

[0025] The foregoing has shown and described the basic principles and main features of this utility model, as well as its advantages. Those skilled in the art should understand that this utility model is not limited to the above embodiments. The embodiments and descriptions in the specification are merely illustrative of the principles of this utility model. Various changes and modifications may be made to this utility model without departing from its spirit and scope. All such changes and modifications fall within the scope of protection of this utility model as defined by the appended claims and their equivalents.

Claims

1. A one-way clutch bearing testing machine, characterized in that: The device includes a tooling table, a hydraulic brake structure, a clutch structure, a main shaft, a mandrel, and an oil tank. The end of the mandrel is inserted into the oil tank, and the end of the mandrel is detachably connected to a one-way clutch bearing to be tested. The beginning of the mandrel is linked to the main shaft through the clutch structure. The mandrel is linked to the hydraulic brake structure, and the hydraulic brake structure provides a reverse torque to the mandrel to simulate the braking condition of the bearing during actual operation. The tooling table is provided with a torque loading structure for applying torque to the mandrel to simulate the torque condition of the bearing during braking. The tooling table is also provided with a drive structure for driving the main shaft to rotate at high speed to simulate the no-load rotation condition of a car during actual operation.

2. The one-way clutch bearing testing machine according to claim 1, characterized in that: The hydraulic brake structure includes a brake disc and a brake caliper for working in conjunction with the brake disc to achieve brake closure or disengagement. The brake disc is coaxially connected to the spindle.

3. The one-way clutch bearing testing machine according to claim 1, characterized in that: The clutch structure includes a pneumatic clutch, wherein the spindle and the main shaft are coaxially and linkedly configured via the pneumatic clutch to achieve closed connection or disconnection of the spindle and the main shaft via the pneumatic clutch.

4. A one-way clutch bearing testing machine according to claim 1, characterized in that: The torque loading structure includes a servo motor, a drive shaft, a diaphragm coupling, and a reducer. The servo motor is mounted on a tooling table and is linked to the drive shaft through the reducer and the diaphragm coupling. The end of the drive shaft is placed in an oil tank and is detachably connected to and coaxially arranged with the spindle.

5. A one-way clutch bearing testing machine according to claim 4, characterized in that: The torque loading structure also includes a torque sensor, which is configured in conjunction with the drive shaft.

6. A one-way clutch bearing testing machine according to claim 1, characterized in that: The drive structure includes a variable frequency motor mounted on a tooling table, and the variable frequency motor is connected to the main shaft by a synchronous belt drive.

7. A one-way clutch bearing testing machine according to claim 1, characterized in that: The oil tank is filled with lubricating oil, the one-way clutch bearing to be tested is immersed in the lubricating oil, the oil tank is equipped with a temperature control structure for detecting the temperature of the lubricating oil, and the oil tank is equipped with a liquid level switch.

8. A one-way clutch bearing testing machine according to claim 7, characterized in that: The temperature control structure includes an electric heating element installed on the oil tank, a temperature sensor for detecting the temperature of the lubricating oil inside the oil tank, and a temperature controller that works in conjunction with the electric heating element to control the temperature of the lubricating oil.

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