Comprehensive performance test bench for tail shaft elastic end face sealing device

Abstract

The utility model relates to a comprehensive performance test bench for a tail shaft elastic end face sealing device. A driving device is used for driving a driving ring and a moving ring to operate according to a set rotating speed; the radial displacement loading device is used for simulating relative radial static and dynamic displacement loading functions between a static ring and a movable ring in the tail shaft elastic end face sealing device to be tested; the axial displacement loading device is used for simulating axial static and dynamic displacement loading functions of the stern shaft; the loading device hydraulic control system is used for controlling the radial displacement loading device and the axial displacement loading device to simulate axial and radial static and dynamic displacement working conditions of the tail shaft elastic end face sealing device to be tested, and the working conditions are measured by a radial displacement sensor and an axial displacement sensor which are arranged in the test bed; and the sealing performance and the friction performance of the tail shaft elastic end face sealing device under the axial and radial static and dynamic displacement working conditions are measured and analyzed through a torque tachometer and a flow meter.

Description

Technical Field

[0001] The utility model relates to a comprehensive performance test platform for a stern shaft elastic end face sealing device of a ship power propulsion system. Background Art

[0002] The stern shaft elastic end face seal is used to seal the part of the propeller-propelled ship shaft passing through the stern tube to isolate seawater from entering the cabin. It is one of the main components of the ship shaft. The performance of the stern shaft elastic end face seal is closely related to the operating state of the stern shaft. It is necessary to test the performance of the stern shaft elastic end face seal on a test bench to simulate the operating conditions, especially different stern shaft operating conditions. The test function of the currently disclosed stern shaft elastic end face seal performance test bench has certain limitations and cannot meet the performance test requirements of the stern shaft elastic end face seal under simulated complex stern shaft operating conditions. For example, the patent disclosed "Dynamic Loading Test Bench for Axial Displacement of Stern Shaft Elastic End Face Sealing Device" (Announcement No. CN218787909U) can only simulate the performance test of the stern shaft elastic end face sealing device under the axial displacement of the stern shaft, but cannot simulate the radial displacement operation condition of the stern shaft. Moreover, since the stern shaft axial displacement loading mechanism is arranged on the entire shaft system, for the performance test bench of the stern shaft elastic end face sealing device with a large shaft diameter, the entire test bench shaft system has a large mass and inertia, and it is difficult to improve the frequency response of the axial motion of the shaft system, and it is impossible to accurately simulate the axial operation condition of the shaft system; in the patent disclosed "A Reliability Test Equipment for Shaft End Face Sealing Device for Ships" (Announcement No. CN114593906A), the axial displacement driving device is connected to the entire driving device, and has a large inertia, and cannot sensitively and accurately control the axial displacement; the radial displacement control has only one vertical direction, and cannot simulate the actual radial displacement demand; the axial displacement and radial displacement control devices can only realize static adjustment, and have no dynamic adjustment function, and cannot better simulate the performance of the stern shaft elastic end face sealing device under actual ship conditions.

[0003] According to the operating characteristics of the ship's stern shaft elastic end face sealing device, it is necessary to design a comprehensive performance test bench for the stern shaft elastic end face sealing device to realize the static and dynamic equipment performance tests of the stern shaft elastic end face sealing device, especially the tests of the equipment performance under the axial and radial static and dynamic displacement conditions of the stern shaft, so as to verify the performance of the stern shaft elastic end face sealing device under the actual ship operating conditions. Summary of the invention

[0004] In order to simulate the actual ship operation conditions of the ship's stern shaft elastic end face sealing device, the performance test of the stern shaft elastic end face sealing device is completed on a test platform. The utility model provides a comprehensive performance test bench for the stern shaft elastic end face sealing device, which realizes the performance test and verification requirements of the stern shaft elastic end face sealing device under the conditions of simulating the stern shaft without axial and radial displacement and axial and radial static and dynamic displacement.

[0005] To achieve the above purpose, the technical solution of the utility model is: a comprehensive performance test bench for a stern shaft elastic end face sealing device, including a drive device, a simulation shaft, a water tank assembly, a radial displacement loading device, an axial displacement loading device, a torque tachometer, a flow meter, a radial displacement sensor, an axial displacement sensor, a loading device hydraulic control system, a tested stern shaft elastic end face sealing device,

[0006] The driving device is connected to the driving ring and the moving ring on the elastic end face sealing device of the tested stern shaft through the simulated shaft 2, and is used to drive the driving ring and the moving ring to run at a set speed;

[0007] A radial displacement loading device, installed on the water tank assembly and acting on the simulated shaft 1 of the driving device, is used to simulate the relative radial static and dynamic displacement loading functions between the static ring and the dynamic ring in the tested stern shaft elastic end face sealing device;

[0008] An axial displacement loading device, connected to the simulation shaft 2, is used to simulate the axial static and dynamic displacement loading functions of the stern shaft;

[0009] The hydraulic control system of the loading device is connected to and controls the radial displacement loading device and the axial displacement loading device, and is used to simulate the axial and radial static and dynamic displacement conditions of the elastic end face sealing device of the stern shaft under test;

[0010] The axial, radial static and dynamic displacements of the stern shaft elastic end face sealing device are measured by radial displacement sensor and axial displacement sensor, and the sealing performance and friction performance of the stern shaft elastic end face sealing device under axial, radial static and dynamic displacement conditions are measured and analyzed by torque tachometer and flowmeter.

[0011] Furthermore, the driving device is composed of a variable frequency motor, a coupling 1, a gear box, a coupling 2, a coupling 3, a thrust bearing, a radial bearing 1, a main shaft, a radial bearing 2, a simulated shaft 1, and a guide shaft. The variable frequency motor is connected to the simulated shaft 1 and the guide shaft through the coupling 1, the gear box, the coupling 2, the coupling 3, and the main shaft.

[0012] Furthermore, a torque speed meter is connected between coupling 2 and coupling 3.

[0013] Furthermore, two sets of independently controllable radial displacement loading devices, vertical and horizontal, are arranged in the comprehensive performance test bench of the stern shaft elastic end face sealing device, and are respectively connected to the hydraulic control systems of the loading devices, so as to control different oil ports in the vertical and horizontal sets of radial displacement loading devices through the hydraulic control system of the loading device, control any position of the static ring in the vertical and horizontal directions of the tested stern shaft elastic end face sealing device, realize any relative radial static and dynamic displacement loading function between the static ring and the dynamic ring in the tested stern shaft elastic end face sealing device, and simulate the radial static and dynamic displacement of the stern shaft of the actual ship of the stern shaft elastic end face sealing device.

[0014] Furthermore, the radial displacement loading device is composed of a radial loading cylinder, a vertical slide, a vertical linear guide, a horizontal slide, and a horizontal linear guide, wherein the vertically installed radial loading cylinder is connected to the vertical slide, and both sides of the vertical slide are placed in the vertical linear guide; the horizontally installed radial loading cylinder is connected to the horizontal slide, and both ends of the horizontal slide are connected to the horizontal linear guide.

[0015] Furthermore, the radial loading cylinder is composed of a radial cylinder piston rod, a radial cylinder end cover 1, a radial cylinder body, a radial cylinder end cover 2, a radial cylinder screw, a radial cylinder locking sleeve, and a radial displacement sensor. The piston of the radial cylinder piston rod is placed in the radial cylinder body, and both ends of the piston rod are connected to the radial cylinder body through the radial cylinder end cover 1 and the radial cylinder end cover 2 respectively, wherein the end face of the radial cylinder body located at one end of the radial cylinder end cover 2 is fixedly connected to the radial cylinder locking sleeve by a radial cylinder screw, and a radial displacement sensor connected to the radial cylinder piston rod is provided in the radial cylinder locking sleeve; the radial cylinder locking sleeve is provided with an oil port K2, and the radial cylinder body is provided with oil ports A2 and B2.

[0016] Furthermore, the hydraulic control system of the loading device is connected to the horizontal radial displacement loading device, and is used to control the oil ports A2, B2, and K2 in the radial displacement loading device, control the radial position of the radial cylinder piston rod, and control the pressure oil in the oil port K2 of the radial displacement loading device, thereby realizing the locking and unlocking functions of the radial cylinder piston rod by the radial cylinder locking sleeve, and finally completing the two functions of static maintenance and dynamic control of the relative radial position of the radial cylinder piston rod and the radial cylinder body.

[0017] Furthermore, the axial displacement loading device is composed of an axial cylinder piston rod, an axial cylinder end cover, an axial cylinder body, an axial cylinder locking sleeve, an axial displacement sensor, a support bearing, and an oil distribution ring assembly. The axial cylinder body is connected to the axial cylinder piston rod through the axial cylinder end cover, the rear end of the axial cylinder body is fixedly connected to the axial cylinder locking sleeve and the axial displacement sensor, and the rear end of the axial cylinder piston rod is connected to the support bearing and the oil distribution ring assembly; the oil distribution ring assembly is provided with oil ports A1, K1, and B1.

[0018] Furthermore, the cylinder piston rod in the axial displacement loading device maintains an axial position under the constraint of the support bearing, the axial cylinder body is connected to the transition flange 2 and the simulated shaft 2, the simulated shaft 2 can slide freely in the axial direction of the guide shaft and rotate with the guide shaft, the axial displacement of the axial cylinder body is consistent with the displacement of the simulated shaft 2, and can simulate the axial static and dynamic displacement functions of the stern shaft of a real ship of the stern shaft elastic end face sealing device.

[0019] Furthermore, the hydraulic control system of the loading device is connected to the axial displacement loading device, and is used to control the oil ports A1, B1, and K1 in the axial displacement loading device, control the axial position of the axial cylinder body, and control the pressure oil in the oil port K1 of the axial displacement loading device, thereby realizing the locking and unlocking functions of the axial cylinder locking sleeve on the axial cylinder piston rod, and finally completing the two functions of static maintenance and dynamic control of the relative axial position of the axial cylinder body and the cylinder piston rod.

[0020] Furthermore, the hydraulic control system of the loading device is composed of a pressure source P1, a pressure source P2, an axial loading cylinder in the axial displacement loading device, a radial loading cylinder in the radial displacement loading device, a servo valve, a one-way valve, a hydraulically controlled one-way valve, a balancing valve, a shut-off reversing valve, and a hydraulically controlled one-way valve. Dual pressure sources P1 and P2 are provided to avoid the pressure in the locking function control ports K1 and K2 in the axial loading cylinder and the radial loading cylinder being affected, thereby ensuring the reliable operation of the locking function in the axial loading cylinder and the radial loading cylinder; two hydraulically controlled one-way valves are provided to maintain the cylinder position of the axial loading cylinder and the radial loading cylinder in static displacement, and to communicate with the axial loading cylinder and the radial loading cylinder. The locking sleeve has dual-position locking and dual insurance functions, which improves the static position stability maintaining function of the axial loading cylinder and the radial loading cylinder. The servo valve cooperates with the stop reversing valve to realize the static and dynamic control of the position of the axial loading cylinder and the radial loading cylinder, and realizes the simulation of the stern shaft without axial and radial displacement and axial, radial static and dynamic displacement conditions; three one-way valves are set to avoid mutual interference in the control between the axial loading cylinder and the radial loading cylinder; two balancing valves are set to reduce the influence of the spring force of the elastic component of the elastic end face sealing device of the tested stern shaft and the gravity force of the elastic end face sealing device of the tested stern shaft and the radial loading device on the displacement control accuracy of the axial loading cylinder and the vertical radial loading cylinder.

[0021] The beneficial effects of the utility model are:

[0022] The utility model discloses a comprehensive performance test bench for a stern shaft elastic end face sealing device, and is designed with drive devices such as a variable frequency motor, a gear box, and a coupling, so as to realize the control of the test rotation speed of the stern shaft elastic end face sealing device; an axial displacement loading device, a radial displacement loading device, and a hydraulic control system are designed in the test bench, so as to realize the performance test and verification requirements of the stern shaft elastic end face sealing device under the conditions of simulating the stern shaft without axial and radial displacement and axial and radial static and dynamic displacement; a torque tachometer, a flow meter, a displacement sensor, and other detection elements are designed in the test bench to test and analyze the sealing performance, friction performance, and other equipment performance of the stern shaft elastic end face sealing device. BRIEF DESCRIPTION OF THE DRAWINGS

[0023] Figure 1 This is a simplified structural diagram of the comprehensive performance test bench for the stern shaft elastic end face sealing device of the utility model;

[0024] Figure 2 yes Figure 1 Structural diagram of the radial displacement loading device;

[0025] Figure 3 yes Figure 2 Structural diagram of the radial loading cylinder;

[0026] Figure 4 yes Figure 1 Structural diagram of the axial displacement loading device;

[0027] Figure 5 This is a schematic diagram of the hydraulic control system of the loading device in the comprehensive performance test bench of the stern shaft elastic end face sealing device of the utility model;

[0028] Figure 6 yes Figure 1 Typical structural diagram of the elastic end face sealing device of the stern shaft under test. DETAILED DESCRIPTION

[0029] The utility model is further described below in conjunction with the accompanying drawings and embodiments.

[0030] like Figures 1 to 6 As shown, a stern shaft elastic end face sealing device comprehensive performance test bench provided by an embodiment of the utility model comprises a variable frequency motor 1, a coupling 1 2, a gear box 3, a coupling 2 4, a torque tachometer 5, a coupling 3 6, a thrust bearing 7, a radial bearing 1 8, a main shaft 9, a radial bearing 2 10, a simulated shaft 1 11, a guide shaft 12, an end cover 13, a screw 14, a water tank assembly 15, a radial displacement loading device 16, a transition flange 1 17, a tested stern shaft elastic end face sealing device 18, a simulated shaft 2 19, a nut 20, a transition flange 2 21, an axial displacement loading device 22, a flow meter 23, a mounting platform assembly 24, a loading device hydraulic control system, and the like.

[0031] The variable frequency motor 1 drives the simulated shaft 2 19 and the driving ring 18.6 and the moving ring 18.5 on the tested stern shaft elastic end face sealing device 18 connected thereto to run at the set speed through the driving device composed of the coupling 1 2, the gear box 3, the coupling 2 4, the torque tachometer 5, the coupling 3 6, the main shaft 9, the simulated shaft 1 11, the guide shaft 12 and other components. The radial displacement sensor 161.7 and the axial displacement sensor 22.8 are used to measure the simulated shaft 2 19 without axial and radial displacement conditions, that is, the elastic component 18.2 on the tested stern shaft elastic end face sealing device 18 is at the set compression amount and the installation seat body 18.1, the elastic component 18.2, the stationary ring seat 18.3, the stationary ring 18.4 and the moving ring 18.5 and the driving ring 18.6 are coaxial. The sealing performance, friction performance and other equipment performance of the stern shaft elastic end face sealing device under the condition of no axial and radial displacement are measured and analyzed through the torque tachometer 5 and the flowmeter 23. The radial displacement loading device 16 and the axial displacement loading device 22 are controlled by the loading device hydraulic control system to simulate the axial and radial static and dynamic displacement conditions and are measured by the radial displacement sensor 161.7 and the axial displacement sensor 22.8. The sealing performance, friction performance and other equipment performance of the stern shaft elastic end face sealing device under the axial and radial static and dynamic displacement conditions are measured and analyzed by the torque tachometer 5 and the flow meter 23.

[0032] like Figure 2 As shown in (a) and (b), the radial displacement loading device 16 is composed of a radial loading cylinder 16.1, a vertical slide 16.2, a vertical linear guide 16.3, a horizontal slide 16.4, a horizontal linear guide 16.5, etc. Among them, the vertically installed radial loading cylinder 16.1a is connected to the vertical slide 16.2, and both sides of the vertical slide 16.2 are placed in the vertical linear guide 16.3; the horizontally installed radial loading cylinder 16.1b is connected to the horizontal slide 16.4, and both ends of the horizontal slide 16.4 are connected to the horizontal linear guide 16.5.

[0033] like Figure 3As shown, the radial loading cylinder 16.1 is composed of a radial cylinder piston rod 161.1, a radial cylinder end cover 1 161.2, a radial cylinder body 161.3, a radial cylinder end cover 2 161.4, a radial cylinder screw 161.5, a radial cylinder locking sleeve 161.6, a radial displacement sensor 161.7, etc. The piston of the radial cylinder piston rod 161.1 is placed in the radial cylinder body 161.3, and the two ends of the piston rod are connected to the radial cylinder body 161.3 through the radial cylinder end cover 1 161.2 and the radial cylinder end cover 2 161.4 respectively, wherein the end face of the radial cylinder body 161.3 located at one end of the radial cylinder end cover 2 161.4 is fixedly connected to the radial cylinder locking sleeve 161.6 by a radial cylinder screw 161.5, and the radial cylinder locking sleeve 161.6 is provided with a radial displacement sensor 161.7 connected to the radial cylinder piston rod 161.1.

[0034] By controlling the pressure oil in the radial loading cylinder oil port K2, the radial cylinder locking sleeve can lock and unlock the radial cylinder piston rod, and finally achieve the two functions of static maintenance and dynamic control of the relative axial position between the radial cylinder piston rod and the radial cylinder body. Two sets of vertical and horizontal independently controllable radial displacement loading devices are set up in the comprehensive performance test bench of the stern shaft elastic end face sealing device. Through the control of the oil ports A2, B2, and K2 in the vertical and horizontal two sets of radial displacement loading devices by the hydraulic system, the vertical and horizontal positions of the static ring in the tested stern shaft elastic end face sealing device can be controlled, and the relative arbitrary radial static and dynamic displacement loading functions between the static ring and the dynamic ring in the tested stern shaft elastic end face sealing device can be realized, simulating the radial static and dynamic displacement of the stern shaft of the actual ship of the stern shaft elastic end face sealing device.

[0035] like Figure 4 As shown, the axial displacement loading device 22 is composed of an axial cylinder piston rod 22.1, an axial cylinder end cover 22.2, an axial cylinder screw 22.3, an axial cylinder body 22.4, an axial cylinder end cover 22.5, an axial cylinder screw 22.6, an axial cylinder locking sleeve 22.7, an axial displacement sensor 22.8, a support bearing 22.9, an oil distribution ring assembly 22.10, etc. One end of the axial oil cylinder body 22.4 is fixedly connected to the simulation shaft 2 19 through the transition flange 21, and the axial oil cylinder piston rod 22.1 is connected to the axial oil cylinder body 22.4 through the axial oil cylinder end cover 1 22.2 and the axial oil cylinder end cover 22.5. The rear end of the axial oil cylinder body 22.4 is fixedly connected to the axial oil cylinder locking sleeve 22.7 and the axial displacement sensor 22.8. One end of the axial oil cylinder piston rod 22.1 is connected to the guide shaft 12, and the other end is connected to the support bearing 22.9 and the oil distribution ring assembly 22.10. The oil distribution ring assembly 22.10 is provided with oil ports A1, K1, and B1.

[0036] By controlling the pressure oil in the oil port K1 of the axial displacement loading device 22, the locking and unlocking functions of the axial cylinder locking sleeve on the axial cylinder piston rod are realized, and finally the two functions of static maintenance and dynamic control of the relative axial position of the axial cylinder body and the cylinder piston rod are completed. The cylinder piston rod in the axial displacement loading device 22 maintains the axial position under the constraint of the support bearing 22.9, and the axial position of the axial cylinder body 22.4 is controlled by the hydraulic system to control the oil ports A1, B1, and K1 in the axial displacement loading device 22; the axial cylinder body 22.4 is connected with the transition flange 21 and the simulation shaft 219, and the simulation shaft 216 can slide freely in the axial direction of the guide shaft 12 and rotate with the guide shaft. The axial displacement of the axial cylinder body 22.4 is consistent with the displacement of the simulation shaft 219, which can simulate the static and dynamic displacement functions of the axial stern shaft of the stern shaft elastic end face sealing device of the real ship. The overall mass of the axial moving parts in the axial displacement loading device 22 is relatively small, which can improve the dynamic frequency response of the simulated axial displacement and better verify the performance of the stern shaft elastic end face sealing device.

[0037] like Figure 5 As shown, the hydraulic control system of the loading device consists of a pressure source P1, a pressure source P2, an axial loading cylinder C1 in the axial displacement loading device, radial loading cylinders C2.1 and C2.2 in the radial displacement loading device, a servo valve V1, a check valve V2, a hydraulically controlled check valve V3.1 and V3.2, a balancing valve V4, a check valve V5.1 to V5.3, a stop reversing valve V6.1 to V6.3, a servo valve V7.1 and V7.2, a check valve V8.1 and V8.2, a hydraulically controlled check valve V9.1 to V9.4, a balancing valve V10, etc.

[0038] like Figure 6 As shown, the typical structure of the tested stern shaft elastic end face sealing device 18 is composed of a mounting seat body 18.1, an elastic component 18.2, a stationary ring seat 18.3, a stationary ring 18.4, a dynamic ring 18.5, a driving ring 18.6, etc.

[0039] By setting up dual pressure sources P1 and P2, the pressure in the locking function control ports K1 and K2 of the axial loading cylinder and radial loading cylinder is prevented from being affected, and the reliable operation of the locking function of the axial loading cylinder and radial loading cylinder is ensured. The setting of hydraulically controlled one-way valves V3 and V9 can maintain the cylinder position of the axial loading cylinder and radial loading cylinder in static displacement, and can perform dual-position locking and dual insurance functions with the locking sleeves in the axial loading cylinder and radial loading cylinder, thereby improving the static position stability maintenance function of the axial loading cylinder and radial loading cylinder. The servo valves V1 and V7 are used in conjunction with the stop reversing valve V6 to realize the static and dynamic control of the position of the axial loading cylinder and radial loading cylinder, and to simulate the stern shaft without axial and radial displacement and axial and radial static and dynamic displacement conditions. The one-way valves V2, V5, and V8 can avoid mutual interference between the control of the axial loading cylinder and radial loading cylinder. The balancing valves V4 and V10 can reduce the influence of the spring force of the elastic component of the elastic end face sealing device of the tested stern shaft and the gravity force of the elastic end face sealing device of the tested stern shaft and the radial loading device on the displacement control accuracy of the axial loading cylinder and the vertical radial loading cylinder.

[0040] The utility model is a design of a comprehensive performance test bench for a stern shaft elastic end face sealing device. Starting from the operating conditions of the ship stern shaft elastic end face sealing device, the demand for dynamic changes in the test shaft position during the operation of the test shaft is realized, and the sealing performance, friction performance and other equipment performance tests of the stern shaft elastic end face sealing device under different rotation speeds and stern shaft radial and axial static and dynamic displacement simulated operating conditions can be completed.

[0041] like Figure 1 , Figure 2 , Figure 3 , Figure 5As shown, when simulating the working condition of no radial displacement of the stern shaft, the servo valves V7.1 and V7.2 in the hydraulic control system of the loading device are in the middle position, and the stop reversing valves V6.2 and V6.3 are in the power-off state; at this time, the control oil port K2 in the two radial loading cylinders 16.1 (i.e., C2.1 and C2.2) is in the unloading state, and the radial cylinder locking sleeve 161.6 has a locking function for the radial cylinder piston rod 161.1; at the same time, under this working condition, the hydraulically controlled one-way valves V9.1~V9.4 have a locking function for the oil circuits corresponding to the A2 and B2 oil ports of the two radial loading cylinders 16.1, maintain the position of the radial cylinder piston rod 161.1, and have a double locking and double insurance position locking function with the radial cylinder locking sleeve. The static working condition of radial displacement of the stern shaft is simulated by controlling the position change of the mounting seat 18.1 on the elastic end face sealing device 18 of the tested stern shaft; according to the static radial displacement instruction, it is converted into the displacement in the horizontal and vertical directions respectively, and the cut-off reversing valves V6.2 and V6.3 are in the energized state to provide control pressure oil to the control oil port K2 and the hydraulic control one-way valves V9.1~V9.4 in the radial loading cylinder 16.1, unlocking the position locking state of the radial cylinder piston rod 161.1, and controlling the radial cylinder piston rod 161.1 in the horizontal and vertical radial loading cylinders 16.1 through the servo valves V7.1 and V7.2. When the command position is reached, the positions of the vertical slide 16.2 and the horizontal slide 16.4, i.e., the position control of the mounting seat 18.1 on the tested stern shaft elastic end face sealing device 18, are completed; the balancing valve V10 can reduce the influence of the gravity force of the tested stern shaft elastic end face sealing device on the vertical radial displacement control accuracy; the one-way valves V5 and V8 can avoid mutual interference between the hydraulic circuits; after the radial displacement reaches the specified position, the stop reversing valves V6.2 and V6.3 are switched to the power-off state, the servo valves V7.1 and V7.2 are in the middle position, and the cylinder piston rod 161.1 is in the double locking state to ensure the stability of the static radial displacement. The dynamic working condition of stern shaft radial displacement is simulated, which is also achieved by controlling the position change of the mounting seat 18.1 on the elastic end face sealing device 18 of the tested stern shaft; according to the dynamic radial displacement instruction, it is converted into the displacement in the horizontal and vertical directions respectively, and the stop reversing valves V6.2 and V6.3 are in the energized state to provide control pressure oil to the control oil port K2 and the hydraulic control one-way valves V9.1~V9.4 in the radial loading cylinder 16.1, unlocking the position locking state of the radial cylinder piston rod 161.1, and controlling the dynamic position of the radial cylinder piston rod 161.1 in the horizontal and vertical radial loading cylinders 16.1 through the servo valves V7.1 and V7.2 to realize the dynamic radial displacement function.

[0042] like Figure 1 , Figure 4 , Figure 5As shown, when simulating the working condition of no axial displacement of the stern shaft, the servo valve V1 in the hydraulic control system of the loading device is in the middle position, and the stop reversing valve V6.1 is in the power-off state; at this time, the control oil port K1 in the axial loading cylinder C1 in the axial displacement loading device 22 is in the unloading state, and the axial cylinder locking sleeve 22.7 has a locking function on the axial cylinder piston rod 22.1; at the same time, under this working condition, the hydraulically controlled one-way valves V3.1 and V3.2 have a locking function on the oil circuits corresponding to the A1 and B1 oil ports of the axial displacement loading device 22, maintain the position of the axial cylinder body 22.4, and have a double locking and double insurance position locking function with the axial cylinder locking sleeve. The simulation of the static working condition of the stern shaft axial displacement is achieved by controlling the axial position change of the simulated shaft 19; since the simulated shaft 19 is rigidly connected to the transition flange 21, the axial cylinder body 22.4, and the axial cylinder locking sleeve 22.7 by screws, and the axial cylinder piston rod 22.1 maintains the axial position under the constraint of the support bearing 22.9, the axial position control of the simulated shaft 19 can be converted into the axial position control of the axial cylinder body 22.4 relative to the axial cylinder piston rod 22.1; according to the static axial displacement instruction, it is converted into the displacement of the axial cylinder body 22.4, and the shut-off reversing valve V6.1 is in the energized state to move axially The control oil port K1 and the hydraulically controlled one-way valves V3.1 and V3.2 in the loading cylinder C1 provide control pressure oil to unlock the position locking state of the axial cylinder body 22.4, and control the axial cylinder body 22.4 to reach the command position through the servo valve V1; the balance valve V4 can reduce the influence of the spring force of the elastic component of the elastic end face sealing device of the tested stern shaft on the control accuracy of the axial displacement, and the one-way valves V2 and V5 can avoid mutual interference between the hydraulic circuits; after the axial displacement reaches the specified position, the stop reversing valve V6.1 is switched to the power-off state, the servo valve V1 is in the middle position, and the axial cylinder body 22.4 is in the double locking state to ensure the stability of the axial static displacement. The simulation of the dynamic working condition of the stern shaft axial displacement is also achieved by controlling the position change of the axial cylinder body 22.4; according to the dynamic axial displacement instruction, it is converted into the axial displacement of the axial cylinder body 22.4, and the cut-off reversing valve V6.1 is in the energized state to provide control pressure oil to the control oil port K1 and the hydraulically controlled one-way valves V3.1 and V3.2 in the axial loading cylinder C1, unlocking the position locking state of the axial cylinder piston rod 22.1, and controlling the dynamic position of the axial cylinder body 22.4 through the servo valve V1 to realize the dynamic axial displacement function.

[0043] The driving device of the comprehensive performance test bench for the stern shaft elastic end face sealing device can simulate various speed conditions of the stern shaft. The hydraulic control system of the loading device can simultaneously control two sets of vertical and horizontal radial displacement loading devices and axial displacement loading devices to simulate various complex combination conditions of the stern shaft without axial and radial displacement and axial and radial static and dynamic displacement. In addition, the torque tachometer, flow meter, displacement sensor and other components can be used to detect and finally complete the comprehensive performance tests of the sealing performance, friction performance and other comprehensive performance of the stern shaft elastic end face sealing device under different working conditions.

Claims

1. A comprehensive performance test bench for a stern shaft elastic end face seal device, characterized in that: It includes a drive device, a simulated shaft, a water tank assembly, a radial displacement loading device, an axial displacement loading device, a torque tachometer, a flow meter, a radial displacement sensor, an axial displacement sensor, a loading device hydraulic control system, and a tested stern shaft elastic end face sealing device. The driving device is connected to the driving ring and the moving ring on the elastic end face sealing device of the tested stern shaft through the simulated shaft 2, and is used to drive the driving ring and the moving ring to run at a set speed; The radial displacement loading device is installed on the water tank assembly and is used to simulate the relative radial static and dynamic displacement loading functions between the static ring and the dynamic ring in the stern shaft elastic end face sealing device under test; An axial displacement loading device, connected to the simulation shaft 2, is used to simulate the axial static and dynamic displacement loading functions of the stern shaft; The hydraulic control system of the loading device is connected and controls the radial displacement loading device and the axial displacement loading device, and is used to simulate the axial and radial static and dynamic displacement conditions of the elastic end face sealing device of the stern shaft under test; The axial, radial static and dynamic displacements of the stern shaft elastic end face sealing device are measured by radial displacement sensor and axial displacement sensor. The sealing performance and friction performance of the stern shaft elastic end face sealing device under axial, radial static and dynamic displacement conditions are measured and analyzed by torque tachometer and flowmeter.

2. The comprehensive performance test bench for the stern shaft elastic end face sealing device according to claim 1 is characterized by: The driving device is composed of a variable frequency motor, a coupling 1, a gear box, a coupling 2, a coupling 3, a thrust bearing, a radial bearing 1, a main shaft, a radial bearing 2, a simulated shaft 1, and a guide shaft. The variable frequency motor is connected to the simulated shaft 1 and the guide shaft through the coupling 1, the gear box, the coupling 2, the coupling 3, and the main shaft.

3. The comprehensive performance test bench for the stern shaft elastic end face sealing device according to claim 2 is characterized by: A torque speed meter is connected between coupling two and coupling three.

4. The comprehensive performance test bench for the stern shaft elastic end face sealing device according to claim 1 is characterized by: Two sets of independently controllable radial displacement loading devices, vertical and horizontal, are arranged in the comprehensive performance test bench of the stern shaft elastic end face sealing device, and are respectively connected to the hydraulic control system of the loading devices, so as to control different oil ports in the vertical and horizontal sets of radial displacement loading devices through the hydraulic control system of the loading device, control any position of the static ring in the vertical and horizontal directions of the tested stern shaft elastic end face sealing device, realize any relative radial static and dynamic displacement loading function between the static ring and the dynamic ring in the tested stern shaft elastic end face sealing device, and simulate the radial static and dynamic displacement of the stern shaft of the actual ship of the stern shaft elastic end face sealing device.

5. The comprehensive performance test bench for the stern shaft elastic end face sealing device according to claim 1, characterized in that: The radial displacement loading device consists of a radial loading cylinder, a vertical slide, a vertical linear guide, a horizontal slide, and a horizontal linear guide. The vertically installed radial loading cylinder is connected to the vertical slide, and both sides of the vertical slide are placed in the vertical linear guide; the horizontally installed radial loading cylinder is connected to the horizontal slide, and both ends of the horizontal slide are connected to the horizontal linear guide.

6. The comprehensive performance test bench for the stern shaft elastic end face sealing device according to claim 5, characterized in that: The radial loading cylinder is composed of a radial cylinder piston rod, a radial cylinder end cover 1, a radial cylinder body, a radial cylinder end cover 2, a radial cylinder screw, a radial cylinder locking sleeve, and a radial displacement sensor. The piston of the radial cylinder piston rod is placed in the radial cylinder body, and both ends of the piston rod are connected to the radial cylinder body through the radial cylinder end cover 1 and the radial cylinder end cover 2 respectively. Among them, the end face of the radial cylinder body located at one end of the radial cylinder end cover 2 is fixedly connected to the radial cylinder locking sleeve by the radial cylinder screw, and the radial cylinder locking sleeve is provided with a radial displacement sensor connected to the radial cylinder piston rod; the radial cylinder locking sleeve is provided with an oil port K2, and the radial cylinder body is provided with oil ports A2 and B2.

7. The comprehensive performance test bench for the stern shaft elastic end face sealing device according to claim 4 or 6, characterized in that: The hydraulic control system of the loading device is connected to the horizontal radial displacement loading device, and is used to control the oil ports A2, B2, and K2 in the radial displacement loading device, control the radial position of the radial cylinder piston rod, and control the pressure oil in the oil port K2 of the radial displacement loading device, so as to realize the locking and unlocking functions of the radial cylinder locking sleeve on the radial cylinder piston rod, and finally complete the two functions of static maintenance and dynamic control of the relative radial position of the radial cylinder piston rod and the radial cylinder body.

8. The comprehensive performance test bench for the stern shaft elastic end face sealing device according to claim 1, characterized in that: The axial displacement loading device consists of an axial cylinder piston rod, an axial cylinder end cover, an axial cylinder body, an axial cylinder locking sleeve, an axial displacement sensor, a support bearing, and an oil distribution ring assembly. The axial cylinder body is connected to the axial cylinder piston rod through the axial cylinder end cover, the rear end of the axial cylinder body is fixedly connected to the axial cylinder locking sleeve and the axial displacement sensor, and the rear end of the axial cylinder piston rod is connected to the support bearing and the oil distribution ring assembly; the oil distribution ring assembly is provided with oil ports A1, K1, and B1.

9. The comprehensive performance test bench for the stern shaft elastic end face sealing device according to claim 8, characterized in that: The piston rod of the cylinder in the axial displacement loading device maintains the axial position under the constraint of the support bearing. The axial cylinder body is connected with the transition flange 2 and the simulated shaft 2. The simulated shaft 2 can slide freely in the axial direction of the guide shaft and rotate with the guide shaft. The axial displacement of the axial cylinder body is consistent with the displacement of the simulated shaft 2, which can simulate the axial static and dynamic displacement functions of the stern shaft of a real ship of the stern shaft elastic end face sealing device.

10. The comprehensive performance test bench for the stern shaft elastic end face sealing device according to claim 8, characterized in that: The hydraulic control system of the loading device is connected to the axial displacement loading device, and is used to control the oil ports A1, B1, and K1 in the axial displacement loading device, control the axial position of the axial cylinder body, and control the pressure oil in the oil port K1 of the axial displacement loading device, so as to realize the locking and unlocking functions of the axial cylinder locking sleeve on the axial cylinder piston rod, and finally complete the two functions of static maintenance and dynamic control of the relative axial position of the axial cylinder body and the cylinder piston rod.

11. The comprehensive performance test bench for the stern shaft elastic end face sealing device according to claim 1, characterized in that: The hydraulic control system of the loading device is composed of a pressure source P1, a pressure source P2, an axial loading cylinder in the axial displacement loading device, a radial loading cylinder in the radial displacement loading device, a servo valve, a one-way valve, a hydraulically controlled one-way valve, a balancing valve, a shut-off reversing valve, and a hydraulically controlled one-way valve. Dual pressure sources P1 and P2 are set to avoid the pressure in the locking function control ports K1 and K2 in the axial loading cylinder and the radial loading cylinder being affected, so as to ensure the reliable operation of the locking function in the axial loading cylinder and the radial loading cylinder; two hydraulically controlled one-way valves are set to maintain the cylinder position of the axial loading cylinder and the radial loading cylinder in static displacement, and to cooperate with the locking function in the axial loading cylinder and the radial loading cylinder. The tight sleeve has dual-position locking and dual insurance functions, which improves the static position stability maintaining function of the axial loading cylinder and the radial loading cylinder. The servo valve cooperates with the stop reversing valve to realize the static and dynamic control of the position of the axial loading cylinder and the radial loading cylinder, and realizes the simulation of the stern shaft without axial and radial displacement and axial, radial static and dynamic displacement conditions; three one-way valves are set to avoid mutual interference in the control between the axial loading cylinder and the radial loading cylinder; two balancing valves are set to reduce the influence of the spring force of the elastic component of the elastic end face sealing device of the tested stern shaft and the gravity force of the elastic end face sealing device of the tested stern shaft and the radial loading device on the displacement control accuracy of the axial loading cylinder and the vertical radial loading cylinder.

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