A marine electric hatch cover simulation test platform

Abstract

The application relates to the technical field of ship and ocean engineering equipment testing, in particular to a marine electric hatch cover simulation test platform, which comprises a test rack main body, a hatch cover mechanism, a flatness simulation mechanism, an electric control monitoring box and a power supply driving station. The test rack main body is provided with a test track and an inner track cavity with an electro-hydraulic push rod; the hatch cover mechanism is combined on the test track and adjusts the friction resistance characteristics of the contact surface through an internal simulation unit; the flatness simulation mechanism is arranged in the inner track cavity and can dynamically lift the protrusions on the surface of the test track. The application equivalently restores the friction degradation and the increase of the system reference resistance caused by corrosion and salt dirt under the harsh marine environment through a simulation unit, and cooperates with the flatness simulation mechanism to simulate the physical unevenness of the track, overcomes the test blind area of the existing conventional test which can only run in a clean level state, and realizes the effectiveness detection of the device load and driving capacity.

Description

Technical Field

[0001] This application relates to the field of ship and marine engineering equipment testing technology, and in particular to a simulated test platform for a marine electric hatch cover. Background Technology

[0002] In the field of shipbuilding and marine engineering, large bulk carriers commonly use electro-hydraulic integrated hatch cover lifting devices for opening and closing cargo holds. This device highly integrates the drive motor, hydraulic pump, valve block, and actuator hydraulic cylinder into a single unit. Its main function is to lift hatch covers weighing tens or even hundreds of tons during loading and unloading at port, and to achieve horizontal movement and opening / closing along deck tracks using bottom rollers. Currently, existing electro-hydraulic integrated lifting devices in the industry typically undergo performance verification on a conventional horizontal test bench with rigid counterweights before leaving the factory.

[0003] During long-term navigation and operation of ships and marine engineering projects, the rollers and tracks of hatch covers are exposed to the harsh marine environment of high salt spray and high humidity. The surface of the rollers and tracks is prone to rust, salt crystallization and silt adhesion, which gradually changes its inherent friction characteristics, resulting in an increase in the system's reference resistance. Consequently, in actual operation, the motor load of the drive system slowly increases with the increase of usage time. However, under the existing test conditions, the test track surface is smooth and clean, the test bench is kept in a horizontal state, and the conventional inspection mainly focuses on testing the rated vertical lifting thrust, translation driving force and basic functions of the lifting device in the new machine state, which has a test blind spot.

[0004] Therefore, it is necessary to provide a simulation test platform for marine electric hatch covers to solve the above problems. Summary of the Invention

[0005] The purpose of this application is to provide a simulated test platform for marine electric hatch covers, thereby solving the problem of blind spots in existing conventional horizontal slide test methods due to the difficulty in replicating the real environment.

[0006] To achieve the above objectives, this application provides a marine electric hatch cover simulation test platform, including a test bench body, a test track and a track cavity inside the test track, an electro-hydraulic actuator fixed inside the track cavity, and a track embedding block fixed to the telescopic end of the electro-hydraulic actuator to provide a foundation for lifting tests; The hatch cover mechanism is movably closed on the test track. It includes an opening and closing unit and a simulation unit, which are used to translate along the test track during the test and adjust the frictional resistance characteristics of the contact surface through the simulation unit. A flatness simulation mechanism is installed inside the track cavity to dynamically push up protrusions on the smooth test track surface to simulate the physical unevenness of the track surface. The electrical control monitoring box and the power supply drive station are both located on one side of the main body of the test bench, and are used to control the overall test actions of the device and drive its energy.

[0007] Preferably, in the above technical solution, the opening and closing unit includes a hatch cover, a traveling rack, a fixed frame, and a displacement drive motor. The hatch cover is closed on the test track, the traveling rack is fixed to the bottom surface of the hatch cover, the fixed frame is fixed to the side of the test track, and the displacement drive motor is vertically fixed on the fixed frame, with a drive gear fixed at its output end. The drive gear is adapted to mesh with the traveling rack to drive the hatch cover to move horizontally.

[0008] Preferably, in the above technical solution, the simulation unit includes a walking roller and a friction pad. Several walking rollers are provided on both sides of the hatch cover. Two friction pads are symmetrically fitted onto the outside of the walking rollers and joined together to form a circle. Both ends of the friction pads have insertion blocks, and the walking rollers have notches for the insertion blocks to pass through, which are used to simulate friction performance under different environments by replacing friction pads with different friction coefficients.

[0009] Preferably, in the above technical solution, the simulation unit further includes a locking mechanism. An installation chamber is provided on the side of the traveling roller, and the locking mechanism is disposed within the installation chamber. The locking mechanism includes a mounting base, a rotating handle, a rotating shaft, and a hinged hanging rod. The mounting base is installed within the installation chamber. One end of the rotating handle is rotatably mounted on the mounting base. The rotating shaft is rotatably mounted on the rotating handle, and the hinged hanging rod is rotatably mounted on the rotating shaft, for quickly fastening the friction pad.

[0010] Preferably, in the above technical solution, one end of the insertion block that passes through the notch is fixed with a hook end, which is adapted to cooperate with the hinged hanging rod for locking, so as to realize the quick disassembly and fastening of the friction pad.

[0011] Preferably, in the above technical solution, the flatness simulation mechanism is provided in several groups, including a concave guide frame, a long transmission shaft and several rotating cams. The concave guide frame is fixedly installed in the inner cavity of the track, the long transmission shaft is rotatably installed on the concave guide frame, and several rotating cams are spaced apart along the long transmission shaft to convert the axial rotational torque into an upward eccentric thrust.

[0012] Preferably, in the above technical solution, the flatness simulation mechanism further includes a lifting block and a guide rod. The lifting block is disposed through the horizontal end of the concave guide frame via the guide rod. The lifting block is parallel to the horizontal end of the concave guide frame. A return spring is sleeved on the guide rod. The two ends of the return spring are respectively connected between the lifting block and the horizontal end of the concave guide frame, and are used to achieve lifting and automatic reset under the push of the rotating cam.

[0013] Preferably, in the above technical solution, the flatness simulation mechanism further includes protrusions. A plurality of protrusions are arranged at intervals on the upper surface of the lifting block, and the initial height of each protrusion is different. The protrusions are movably disposed through the test track and are used to pass through the test track surface as the lifting block moves upward, so as to simulate uneven pits and depressions.

[0014] Preferably, in the above technical solution, the flatness simulation mechanism further includes a jack, a linear rack, and a rotary gear. The jack is servo-controlled and fixed inside the track cavity. The linear rack is fixed to the output end of the jack and is used to provide a horizontal linear reciprocating driving force. The rotary gear is coaxially sleeved on one end of the transmission shaft, and the rotary gear meshes with the linear rack to convert linear motion into rotational motion that drives the transmission shaft.

[0015] Preferably, in the above technical solution, the tilt simulation mechanism is symmetrically arranged in two sets, including a support base, a transmission screw, a power motor, a transmission slider, and a lifting link. The support base is horizontally disposed at the bottom of the test track, and one end of the test track is hinged to the corresponding end of the support base. The transmission screw is horizontally disposed on the support base via a bearing. The power motor is fixed to one end of the support base, and its output end is connected to the transmission screw. The transmission slider is threadedly connected to the transmission screw and is horizontally slidably disposed on the support base. One end of the lifting link is hinged to the transmission slider, and the other end is hinged to the bottom surface of the test track, for converting the horizontal displacement of the transmission slider into driving the test track to pitch around its hinged end, so as to achieve tilt angle adjustment.

[0016] Compared with existing technologies, this application has the following advantages: 1. By setting up a hatch cover mechanism with opening and closing units and simulation units on the test track, the frictional resistance characteristics of the contact surface can be dynamically adjusted during the translation test. This design effectively simulates the surface corrosion and increased reference running resistance caused by the hatch cover rollers being exposed to the harsh marine environment for a long time, providing a realistic working condition basis for evaluating the load margin of the lifting drive device.

[0017] 2. By adding a flatness simulation mechanism based on cam pushing and spring reset inside the track cavity, protrusions of varying heights can be dynamically lifted on the originally smooth test track surface. This structure realistically simulates the physical unevenness caused by salt scale crystallization and silt adhesion during actual ship operation, and is suitable for testing the impact resistance and buffering capacity of electro-hydraulic actuators and track components.

[0018] 3. By symmetrically setting up a tilting simulation mechanism consisting of a transmission screw, slider, and connecting rod at the bottom of the test track, the test track can be driven to pitch around its hinge end, achieving precise adjustment of the tilt angle. This effectively simulates the heeling attitude of a ship in wind and waves and the resulting asymmetrical off-center load state at the end of the track.

[0019] 4. By combining the closed-loop control of the electrical control monitoring box and the power supply drive station, this device breaks through the limitation of conventional testing, which can only perform basic tests under ideal working conditions of smoothness, cleanliness and absolute level. It realizes the composite equivalent simulation of multiple adverse factors such as environmental friction degradation, dynamic mechanical impact and attitude tilting and off-center loading. Attached Figure Description

[0020] Figure 1 This is a schematic diagram of the overall structure of the marine electric hatch cover simulation test platform in this application; Figure 2 For this application Figure 1 Schematic diagram of a local structure Figure 3 For this application Figure 2 Enlarged structural diagram at point A in the diagram; Figure 4 For this application Figure 2 Schematic diagram of the hatch cover mechanism; Figure 5 For this application Figure 4 A partial structural diagram of the hatch cover mechanism; Figure 6 For this application Figure 5 Enlarged structural diagram at point B in the diagram; Figure 7 For this application Figure 6 Enlarged structural diagram at point C; Figure 8 For this application Figure 4 A schematic diagram of the bottom structure; Figure 9 For this application Figure 8 Enlarged structural diagram at point D in the diagram; Figure 10 For this application Figure 4 Schematic diagram of the traveling roller structure; Figure 11 For this application Figure 10Enlarged structural diagram at point E in the diagram; Figure 12 For this application Figure 1 Schematic diagram of the inclined simulation mechanism.

[0021] In the attached diagram: 1. Test bench body; 11. Test track; 12. Track cavity; 13. Electro-hydraulic actuator; 14. Track embedding block; 2. Hatch cover mechanism; 21. Hatch cover body; 22. Traveling rack; 23. Fixed frame; 24. Shifting drive motor; 241. Drive gear; 25. Traveling roller; 251. Mounting chamber; 26. Mounting base; 261. Rotating handle; 27. Rotating shaft; 28. Hinge hanging rod; 29. ​​Friction pad; 291. Socket block; 3. Electrical control monitoring box; 4. Power supply drive station; 5. Flatness simulation mechanism; 51. Concave guide frame; 52. Transmission long shaft; 53. Rotary cam; 54. Lifting block; 541. Guide rod; 55. Protruding block; 56. Jack; 57. Linear rack; 58. Rotary gear; 6. Inclined simulation mechanism; 61. Bearing base; 62. Transmission screw; 63. Power motor; 64. Transmission slider; 65. Lifting linkage. Detailed Implementation

[0022] The technical solutions of the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this application, and not all embodiments. Based on the embodiments of this application, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this application.

[0023] like Figures 1-12 As shown, this embodiment of a marine electric hatch cover simulation test platform includes a test bench body 1, a test track 11, and a track cavity 12 located inside the test track 11. An electro-hydraulic actuator 13 is fixed inside the track cavity 12, and a track embedding block 14 is fixed to the telescopic end of the electro-hydraulic actuator 13 to provide an execution basis for the lifting test. The hatch cover mechanism 2 is movably closed onto the test track 11 and includes an opening and closing unit and a simulation unit for translating along the test track 11 during the test and adjusting the connection through the simulation unit. Frictional resistance characteristics of the contact surface; flatness simulation mechanism 5, set inside the track cavity 12, is used to dynamically lift protrusions on the smooth test track 11 surface to simulate the physical unevenness of the track surface; tilt simulation mechanism 6, set at the bottom of the test track 11, is used to dynamically simulate the off-center load test condition when the test bench body 1 is tilted; electrical control monitoring box 3 and power supply drive station 4 are both set on one side of the test bench body 1, and are used to command control and power drive the overall test action of the device.

[0024] The overall working principle of this device is as follows: In the initial stage of testing, through the commands and energy output of the electrical control monitoring box 3 and the power supply drive station 4, the hatch cover mechanism 2 is activated to move horizontally along the test track 11 or is lifted by the electro-hydraulic push rod 13. To test the load performance of the electro-hydraulic push rod 13 under harsh sea conditions, the operator replaces the friction pad 29 with a specific friction coefficient through the quick-release structure on the simulation unit, increasing the resistance when the hatch cover mechanism 2 moves horizontally, simulating the degradation state under long-term salt spray erosion; at the same time, the flatness simulation mechanism 5 is activated, so that local steps or pits are formed on the surface of the test track 11. In addition, in conjunction with the activation of the tilt simulation mechanism 6, the test track 11 is driven to pitch and deflect, simulating the heeling attitude of the hull in wind and waves and the resulting asymmetrical off-center load at the end of the track, thus realizing the performance testing of the lifting device and the electro-hydraulic push rod 13.

[0025] To ensure the continuity of transmission for the hatch cover mechanism 2 during translational drive on test track 11 and during lifting operations, refer to the attached... Figures 1-3 and Figure 8 As shown, the opening and closing unit includes a hatch cover 21, a traveling rack 22, a fixed frame 23, and a displacement drive motor 24. The hatch cover 21 is closed on the test track 11. The traveling rack 22 is fixed to the bottom surface of the hatch cover 21. The fixed frame 23 is fixed to the side of the test track 11. The displacement drive motor 24 is vertically fixed on the fixed frame 23, and its output end is fixed with a drive gear 241. The drive gear 241 is adapted to mesh with the traveling rack 22 to drive the hatch cover 21 to move horizontally.

[0026] It is particularly noteworthy that the front end of the traveling rack 22 has several elongated teeth that extend vertically. When the hatch cover 21 is at the end position of the fully enclosed test bench body 1, the traveling rack 22 maintains engagement with the drive gear 241 precisely because of the elongated teeth at its front end. This design ensures that when the hatch cover 21 is in a closed state and undergoes a vertical lifting test by the electro-hydraulic push rod 13, the travel compensation margin provided by the elongated teeth in the height direction allows the traveling rack 22 to maintain reliable engagement with the stationary drive gear 241 even after the hatch cover 21 is lifted as a whole. This not only avoids the risk of uncontrolled slippage caused by the gear and rack separating during the lifting action, but also ensures that the system can directly switch to the translation test without cumbersome re-alignment operations after the lifting test, achieving seamless connection and safe interlocking between lifting and translation tests.

[0027] During the translation test, the electronic control system controls the displacement drive motor 24 to rotate in both directions. The power output is directly transmitted to the traveling rack 22 through the drive gear 241, which pushes the hatch cover 21, which has a counterweight of tens of tons, to slide smoothly along the test track 11.

[0028] To achieve dynamic adjustment and simulation of frictional performance under marine conditions during testing, refer to the appendix. Figures 9-10 As shown, the simulation unit includes a walking roller 25 and a friction pad 29. Several walking rollers 25 are provided on both sides of the hatch cover 21. Two friction pads 29 are symmetrically fitted on the outside of the walking rollers 25 and joined together to form a circle. Both ends of the friction pads 29 have insertion blocks 291, and the walking rollers 25 have notches for the insertion blocks 291 to pass through.

[0029] Meanwhile, the simulation unit also includes a locking mechanism. The side of the traveling roller 25 has an installation chamber 251. The locking mechanism is set in the installation chamber 251. The locking mechanism includes an installation base 26, a rotating handle 261, a rotating shaft 27, and a hinged hanging rod 28. The installation base 26 is installed in the installation chamber 251. One end of the rotating handle 261 is rotatably mounted on the installation base 26. The rotating shaft 27 is rotatably mounted on the rotating handle 261. The hinged hanging rod 28 is rotatably mounted on the rotating shaft 27. One end of the insertion block 291 that passes through the notch is fixed with a hook end. The hook end is suitable for locking with the hinged hanging rod 28 to realize the quick disassembly and fastening of the friction pad 29.

[0030] During aging or corrosion friction resistance testing, operators do not need to use heavy tools to disassemble the entire traveling roller 25. They only need to turn the rotary handle 261, hidden inside the mounting chamber 251, outwards. Utilizing its over-dead-point self-locking mechanical linkage principle, the hinged hanging rod 28 opens and releases the hook end of the insertion block 291, allowing the original friction pad 29 to be quickly peeled off from the outer edge of the roller. After replacing it with a test-specific friction pad 29 with a rougher surface and higher friction damping, the tensioning and locking are completed by pressing the rotary handle 261 in the opposite direction.

[0031] To simulate the dynamic load impact of a real ship's hatch cover encountering localized salt deposits or rail corrosion protrusions during operation, refer to the attached... Figures 4-6 As shown, the flatness simulation mechanism 5 is provided with several components, including a concave guide frame 51, a long drive shaft 52, and several rotating cams 53. The concave guide frame 51 is fixedly installed in the inner cavity 12 of the track, the long drive shaft 52 is rotatably installed on the concave guide frame 51, and several rotating cams 53 are spaced apart along the long drive shaft 52.

[0032] The flatness simulation mechanism 5 also includes a lifting block 54 and a guide rod 541. The lifting block 54 is installed through the horizontal end of the concave guide frame 51 via the guide rod 541. The lifting block 54 is parallel to the horizontal end of the concave guide frame 51. A return spring is sleeved on the guide rod 541. The two ends of the return spring are respectively connected between the lifting block 54 and the horizontal end of the concave guide frame 51.

[0033] Several protrusions 55 are arranged at intervals on the upper surface of the lifting block 54, and the initial height of each protrusion 55 is different. The protrusions 55 are set through the test track 11.

[0034] As a power source, the flatness simulation mechanism 5 also includes a jack 56 and a linear rack 57. The jack 56 is servo-controlled and fixed inside the track cavity 12. The linear rack 57 is fixed at the output end of the jack 56. The rotating gear 58 is coaxially sleeved on one end of the transmission shaft 52, and the rotating gear 58 and the linear rack 57 mesh with each other.

[0035] During testing, the electronic control system issues commands to extend or retract the jack 56, causing the linear rack 57 to translate. Through the meshing transmission of the rack and pinion, the linear motion is converted into the rotational motion of the rotating gear 58, which in turn drives the transmission shaft 52 and the rotating cam 53 to rotate. The eccentric profile of the cam pushes the lifting block 54 upward against the elastic force of the return spring. At this time, the protrusions 55 of different heights will protrude from the originally smooth surface of the test track 11. Because a purely mechanical linkage mechanism combining cam lifting and rigid spring-guided return is adopted, it can not only withstand the vertical gravity of the crushing stage of the hatch cover under heavy load, but also simulate the unevenness caused by foreign matter agglomeration on the surface of the actual ship track, adapting to the impact resistance and buffering capacity of the test drive system and the electro-hydraulic push rod 13.

[0036] To simulate the heeling attitude of a ship under wind, waves, and sea conditions, refer to the appendix. Figure 1 and Figure 12 As shown, and the resulting asymmetric off-center load condition of the test track 11 and the lifting system, the tilting simulation mechanism 6 is symmetrically arranged in two sets, including a bearing base 61, a transmission screw 62, a power motor 63, a transmission slider 64, and a lifting link 65. The bearing base 61 is horizontally set at the bottom of the test track 11, and one end of the test track 11 is hinged to the corresponding end of the bearing base 61 by a pin to form the rotation fulcrum for the variable pitch of the test track 11; the transmission screw 62 is horizontally rotatably mounted on the bearing base 61 through a bearing; the power motor 63 is fixed at one end of the bearing base 61, and its power output end is coaxially connected to the transmission screw 62; the transmission slider 64 has a threaded hole inside, which is threadedly connected to the transmission screw 62, and the bottom surface of the transmission slider 64 is horizontally sliding and guided on the bearing base 61; one end (lower end) of the lifting link 65 is hinged to the transmission slider 64, and the other end (upper end) is hinged to the bottom surface of the test track 11.

[0037] During the eccentric loading and tilt angle simulation test, the electrical control monitoring box 3 issues a control command to start the power motor 63. The power motor 63 rotates forward or in reverse, driving the transmission screw 62 to rotate in place. Relying on the transmission principle of the screw and nut pair, the rotational motion of the transmission screw 62 is converted into the horizontal reciprocating linear displacement of the transmission slider 64 along the bearing base 61. During the horizontal translation of the transmission slider 64, the lifting linkage 65 changes its attitude accordingly, thereby converting the horizontal thrust or pull of the transmission slider 64 into a variable amplitude jacking force on the other end of the test track 11, driving the entire test track 11 to deflect around its end hinge point, so as to achieve precise adjustment of the tilt angle of the test track 11. By realistically simulating the uneven force at both ends caused by the hull's roll on the test platform, the safety threshold and reliability testing requirements for the electro-hydraulic jacking system and hatch cover structure under extreme eccentric loading and lateral tension conditions are met.

[0038] The specific workflow is as follows: This device, through the control of the electrical control monitoring box 3 and the power supply drive station 4, realizes multi-condition performance testing of the hatch cover mechanism 2 during translation and lifting. The hatch cover mechanism 2 is placed above the test track 11. The drive gear 241 is driven by the displacement drive motor 24, which meshes with the walking rack 22, driving the hatch cover body 21 to perform translation testing along the test track 11. During the test, the two friction pads 29 mounted on the outside of the walking roller 25 are quickly disassembled and tightened by the locking mechanism consisting of the rotating handle 261, the rotating shaft 27, and the hinged hanging rod 28 inserted into the installation chamber 251. By replacing the friction pads 29 with different friction coefficients, the friction performance of the hatch cover roller in the marine environment can be simulated, and the driving capability of the electro-hydraulic push rod 13 can be effectively tested.

[0039] During this test, the data acquisition module built into the electrical control monitoring box 3 will monitor and record the output current change characteristics of the shift drive motor 24 and the transient pressure curve and pressure fluctuation in the hydraulic circuit of the electro-hydraulic push rod 13 in real time. This will transform the physical load under simulated working conditions into quantifiable data indicators, and realize closed-loop testing of the performance of the lifting device and the electro-hydraulic push rod 13.

[0040] To simulate the physical unevenness of the track surface, this device integrates several sets of flatness simulation mechanisms 5 within the track cavity 12: a servo-controlled jack 56 drives a linear rack 57 to extend and retract, which, through meshing with a rotating gear 58, drives the transmission shaft 52 and the rotating cam 53 above it to rotate; the contour surface of the rotating cam 53 pushes the lifting block 54 to overcome the resistance of the return spring and move up and down along the guide rod 541, causing the protrusion 55 on the upper surface of the lifting block 54 to simultaneously protrude through the surface of the test track 11. By adjusting the protrusion 55, uneven pits and bumps are simulated on the smooth track, thereby simulating the dynamic load impact when a ship's hatch cover encounters localized salt deposits or track corrosion protrusions during operation.

[0041] In addition, to simulate the heeling attitude of the ship in wind and waves and the resulting asymmetrical load on the end of the track, this device is used in conjunction with the tilting simulation mechanism 6 located at the bottom of the test track 11: the control command starts the power motor 63 to drive the transmission screw 62 to rotate, which drives the transmission slider 64 to move horizontally back and forth along the support base 61; the displacement of the transmission slider 64 is converted into a variable amplitude thrust on the other end of the test track 11 through the lifting link 65, which drives the test track 11 to deflect around its hinge end, thereby realizing the dynamic adjustment of the tilt angle of the test track 11.

[0042] During the aforementioned multi-condition composite test, the data acquisition module built into the electrical control monitoring box 3 synchronously monitors and records the output current variation characteristics of the shift drive motor 24, as well as the transient pressure curve and pressure fluctuation in the hydraulic circuit of the electro-hydraulic actuator 13 in real time. This transforms the physical load under simulated conditions into quantifiable and evaluable data indicators, enabling closed-loop testing of the performance of the lifting device and the electro-hydraulic actuator 13 under complex conditions such as extreme off-center loads and lateral clamping.

[0043] The foregoing description of specific exemplary embodiments of this application is for illustrative and explanatory purposes. These descriptions are not intended to limit this application to the precise forms disclosed, and it will be apparent that many changes and variations can be made in accordance with the foregoing teachings. The exemplary embodiments were chosen and described in order to explain the specific principles of this application and its practical application, thereby enabling those skilled in the art to implement and utilize various different exemplary embodiments of this application, as well as various different choices and variations. The scope of this application is intended to be defined by the claims and their equivalents.

Claims

1. A marine electric hatch cover simulation test platform, characterized in that, include: The test bench body (1) has a test track (11) and a track cavity (12) located inside the test track (11). An electro-hydraulic push rod (13) is fixed inside the track cavity (12), and a track embedding block (14) is fixed to the telescopic end of the electro-hydraulic push rod (13) to provide a foundation for the lifting test. The hatch cover mechanism (2) is movably closed on the test track (11). It includes an opening and closing unit and a simulation unit, which are used to translate along the test track (11) during the test and adjust the friction resistance characteristics of the contact surface through the simulation unit. The flatness simulation mechanism (5) is set inside the inner cavity (12) of the track and is used to dynamically push up the protrusion on the smooth surface of the test track (11) to simulate the physical unevenness of the track surface. The tilting simulation mechanism (6) is located at the bottom of the test track (11) and is used to dynamically simulate the off-center load test condition when the main body of the test bench (1) is tilted. The electrical control monitoring box (3) and the power supply drive station (4) are both located on one side of the main body of the test bench (1) and are used to control the overall test action of the device and drive it with energy.

2. The marine electric hatch cover simulation test platform according to claim 1, characterized in that, The opening and closing unit includes a hatch cover (21), a traveling rack (22), a fixed frame (23), and a displacement drive motor (24). The hatch cover (21) covers the test track (11). The traveling rack (22) is fixed to the bottom surface of the hatch cover (21). The fixed frame (23) is fixed to the side of the test track (11). The displacement drive motor (24) is vertically fixed to the fixed frame (23), and its output end is fixed with a drive gear (241). The drive gear (241) is adapted to mesh with the traveling rack (22) to drive the hatch cover (21) to move horizontally.

3. The marine electric hatch cover simulation test platform according to claim 1, characterized in that, The simulation unit includes a walking roller (25) and a friction pad (29). Several walking rollers (25) are provided on both sides of the hatch cover (21). Two friction pads (29) are symmetrically fitted on the outside of the walking rollers (25) and joined together to form a circle. Both ends of the friction pads (29) have insertion blocks (291), and the walking rollers (25) have notches for the insertion blocks (291) to pass through, so as to simulate the friction performance under different environments by replacing friction pads (29) with different friction coefficients.

4. The marine electric hatch cover simulation test platform according to claim 3, characterized in that, The simulation unit also includes a locking mechanism. The side of the walking roller (25) is provided with an installation chamber (251). The locking mechanism is located in the installation chamber (251). The locking mechanism includes an installation base (26), a rotating handle (261), a rotating shaft (27), and a hinged hanging rod (28). The installation base (26) is installed in the installation chamber (251). One end of the rotating handle (261) is rotatably mounted on the installation base (26). The rotating shaft (27) is rotatably mounted on the rotating handle (261). The hinged hanging rod (28) is rotatably mounted on the rotating shaft (27) for quickly fastening the friction pad (29).

5. A marine electric hatch cover simulation test platform according to claim 4, characterized in that, The insertion block (291) has a hook end fixed at one end through the notch. The hook end is adapted to cooperate with the hinged hanging rod (28) for locking, so as to realize the quick disassembly and fastening of the friction pad (29).

6. The marine electric hatch cover simulation test platform according to claim 1, characterized in that, The flatness simulation mechanism (5) is provided with several sets, including a concave guide frame (51), a transmission long shaft (52) and several rotating cams (53). The concave guide frame (51) is fixedly installed in the inner cavity (12) of the track. The transmission long shaft (52) is rotatably installed on the concave guide frame (51). Several rotating cams (53) are spaced along the transmission long shaft (52) to convert the axial rotational torque into an upward eccentric thrust.

7. A marine electric hatch cover simulation test platform according to claim 6, characterized in that, The flatness simulation mechanism (5) further includes a lifting block (54) and a guide rod (541). The lifting block (54) is installed through the horizontal end of the concave guide frame (51) via the guide rod (541). The lifting block (54) is parallel to the horizontal end of the concave guide frame (51). A return spring is sleeved on the guide rod (541). The two ends of the return spring are respectively connected between the horizontal ends of the lifting block (54) and the concave guide frame (51) for lifting and automatic reset under the push of the rotating cam (53).

8. A marine electric hatch cover simulation test platform according to claim 7, characterized in that, The flatness simulation mechanism (5) also includes protrusions (55). Several protrusions (55) are arranged at intervals on the upper surface of the lifting block (54), and the initial height of each protrusion (55) is different. The protrusions (55) are movably inserted through the test track (11) and are used to pass through the surface of the test track (11) as the lifting block (54) moves upward, so as to simulate uneven pits and depressions.

9. A marine electric hatch cover simulation test platform according to claim 6, characterized in that, The flatness simulation mechanism (5) also includes a jack (56), a linear rack (57), and a rotary gear (58). The jack (56) is servo-controlled and fixed inside the inner cavity (12) of the track. The linear rack (57) is fixed to the output end of the jack (56) and is used to provide horizontal linear reciprocating driving force. The rotary gear (58) is coaxially sleeved on one end of the transmission shaft (52), and the rotary gear (58) meshes with the linear rack (57) to convert linear motion into rotational motion that drives the transmission shaft (52).

10. A marine electric hatch cover simulation test platform according to claim 1, characterized in that, The tilting simulation mechanism (6) is symmetrically arranged in two sets, including a support base (61), a transmission screw (62), a power motor (63), a transmission slider (64), and a lifting link (65). The support base (61) is horizontally arranged at the bottom of the test track (11), and one end of the test track (11) is hinged to the corresponding end of the support base (61). The transmission screw (62) is horizontally arranged on the support base (61) through a bearing. The power motor (63) is fixed to the support base (65). One end of the support base (61) and its output end are connected to the transmission screw (62). The transmission slider (64) is threaded on the transmission screw (62) and is horizontally slidably disposed on the support base (61). One end of the lifting link (65) is hinged to the transmission slider (64) and the other end is hinged to the bottom surface of the test track (11). It is used to convert the horizontal displacement of the transmission slider (64) into driving the test track (11) to pitch around its hinge end, so as to achieve tilt angle adjustment.

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