Hydraulic ship lift working door anti-jamming system

Abstract

The present application relates to ship lift technical field, specifically disclose a kind of water-lifting ship lift working small door anti-jam system, and including door groove, slidingly arranged in the working small door body of door groove and the hydraulic hoist for driving working small door body lifting;Counterweight, be arranged on working small door body, for adjusting the total weight of working small door body and left and right side counterweight balance, so that the total weight of working small door body is greater than the maximum friction force suffered in its descending process;Sealing assembly, be arranged on working small door body, for forming sealing between working small door body and door groove;Pressure balance unit, for water upstream approach channel is introduced into gap water cavity before opening working small door body, so as to balance the water pressure difference of working small door body upstream and downstream sides.The water-lifting ship lift working small door anti-jam system of the present application embodiment realizes the smooth descent of working small door by counterweight and pressure balance unit, effectively avoids jam.

Description

Technical Field

[0001] This invention belongs to the field of ship lift technology, specifically relating to an anti-jamming system for the working gate of a hydraulic ship lift. Background Technology

[0002] During the operation of a hydraulic ship lift, the working gate frequently jams during descent. This is due to two main reasons: firstly, the working gate itself exhibits an eccentricity, meaning the weight is unbalanced on both sides, causing one side to jam; secondly, the pressure difference between the upstream and downstream sides of the working gate greatly increases the friction, sometimes exceeding the gate's own weight, thus making descent difficult. Summary of the Invention

[0003] This invention aims to at least partially solve one of the technical problems in related technologies. To this end, embodiments of this invention propose an anti-jamming system for the working gate of a hydraulic ship lift. This system, through counterweights and a pressure balancing unit, achieves smooth descent of the working gate, effectively preventing jamming.

[0004] The anti-jamming system for the working gate of a hydraulic ship lift according to an embodiment of the present invention includes a gate slot, a working gate body slidably disposed within the gate slot, a hydraulic gate opener for driving the working gate body to rise and fall, a counterweight, a sealing assembly, and a pressure balancing unit. The counterweight is disposed on the working gate body and is used to adjust the total weight of the working gate body and the balance of the left and right counterweights, so that the total weight of the working gate body is greater than the maximum frictional force it experiences during descent. The sealing assembly is disposed on the working gate body and is used to form a seal between the working gate body and the gate slot. The pressure balancing unit includes a gap drain pipe, a channel drain pipe, a gap drain valve assembly, a new drain valve assembly, a channel drain valve assembly, and a control system. The working gate body is docked with the upstream horizontal door of the ship-carrying chamber at the docking position, forming a gap water cavity between the two. One end of the gap drain pipe is connected to the gap water cavity, and the other end is connected to the downstream vertical shaft. One end of the navigation channel drainage pipe is connected to the upstream navigation channel, and the other end is connected to the middle of the gap drainage pipe. The gap drainage valve assembly is located at the end of the gap drainage pipe near the gap water chamber, the newly added drainage valve assembly is located at the end of the gap drainage pipe near the downstream vertical shaft, and the navigation channel drainage valve assembly is located on the navigation channel drainage pipe. The control system is used to control the opening and closing of each valve assembly to introduce water from the upstream navigation channel into the gap water chamber before opening the working gate body, thereby balancing the water pressure difference between the upstream and downstream sides of the working gate body.

[0005] This invention effectively solves the problem of the working gate getting stuck due to excessive frictional resistance caused by upstream water pressure by adjusting the counterweight, optimizing the sealing components, and comprehensively setting up the pressure balancing unit, thereby reducing the equipment failure rate.

[0006] Preferably, the control system is configured to respond to the pressurization command from the host computer and perform pressure balancing operations according to a preset linkage sequence: first, control the newly added drain valve group to close to cut off the connection between the gap water chamber and the downstream vertical shaft; after it is closed, automatically control the navigation channel drain valve group to open, so that the water from the upstream navigation channel enters the gap water chamber sequentially through the navigation channel drain pipe and the gap drain pipe; after the pressurization delay meets the set time, automatically control the navigation channel drain valve group and the gap drain valve group to close to isolate and seal the gap water chamber after pressurization balancing.

[0007] Preferably, after the water pressure in the gap water cavity is balanced with the water pressure in the upstream navigation channel, the control system controls the hydraulic gate opener to drive the working gate body to descend.

[0008] Preferably, the control system is further configured to respond to a water discharge command from the host computer and control the opening of the gap drain valve group and the newly added drain valve group to discharge the water in the gap water chamber to the downstream vertical shaft through the gap drain pipeline.

[0009] Preferably, the increase in the counterweight is calculated based on the maximum sliding friction force determined by the product of the maximum water pressure and the coefficient of friction on the working gate body, and the original total weight of the working gate body. The increase in the counterweight is not less than the difference between the maximum sliding friction force and the original total weight.

[0010] Preferably, the door groove is a cleaned door groove that has undergone cleaning treatment, and there are no visible particles with a diameter of ≥1cm remaining in the cleaned door groove.

[0011] Preferably, the gap drain valve group, the new drain valve group, and the navigation channel drain valve group are all composed of two electric valves connected in series.

[0012] Preferably, the sealing assembly includes a side water seal and a bottom water seal, wherein the compression of the side water seal with the corresponding water seal seat is 2 mm to 4 mm, and the compression of the bottom water seal with the corresponding water seal seat is 6 mm to 10 mm.

[0013] Preferably, the sealing assembly further includes a guide wheel pad disposed between the working door body and the guide wheel.

[0014] Preferably, the set time is 240 seconds; the control system is a host computer sequential control system, used to realize remote "one-click pressurization" control, the host computer sequential control system has the function of valve position feedback signal acquisition, and its signal feedback delay is ≤1 second, and the fault alarm response time is ≤2 seconds.

[0015] The anti-jamming system for the working gate of the hydraulic ship lift provided by the present invention has the following beneficial effects.

[0016] First, by setting counterweights on the working gate body and reasonably calculating the increase in counterweight, the total weight of the working gate body is made greater than the maximum sliding friction force during the descent, ensuring that the working gate body can descend smoothly by its own weight.

[0017] Second, by introducing water from the upstream navigation channel into the gap water cavity before opening the working gate body through the pressure balancing unit, the water pressure difference between the upstream and downstream sides of the working gate body is balanced, significantly reducing the unbalanced water pressure acting on the working gate body, thereby greatly reducing the frictional resistance during descent and further reducing the risk of jamming.

[0018] Third, the control system automatically executes the leveling and pressurization operation according to the preset linkage sequence, realizing the full-process automated control from valve closing, valve opening, delay to isolation and closure. The operator only needs to send an instruction once on the host computer to complete the operation, without having to go to the site to manually operate the valve, eliminating the safety risks of working near the edge and in the air. At the same time, the leveling and pressurization time is shortened from about 20 minutes for manual operation to less than 8 minutes, which effectively improves the operating efficiency of the ship lift and shortens the time for ships to pass through the dam. Attached Figure Description

[0019] Figure 1 This is a schematic diagram of the overall structure of the working gate of the present invention.

[0020] Figure 2 This is a schematic diagram of the pressure balancing unit of the present invention.

[0021] Figure label:

[0022] 1. Door groove; 2. Hydraulic gate hoist; 3. Small door body; 4. Counterweight; 5. Pressure balancing unit; 51. Gap drain pipe; 52. Navigation channel drain pipe; 53. Gap drain valve assembly; 54. Newly added drain valve assembly; 55. Navigation channel drain valve assembly; 56. Gap water chamber; 6. The uppermost door of the ship's compartment is lowered. Detailed Implementation

[0023] Embodiments of the present invention are described in detail below, examples of which are illustrated in the accompanying drawings. The embodiments described below with reference to the accompanying drawings are exemplary and intended to explain the present invention, and should not be construed as limiting the present invention.

[0024] like Figures 1-2 As shown, the anti-jamming system for the working gate of the hydraulic ship lift of this invention includes a gate slot 1, a working gate body 3 slidably disposed in the gate slot 1, and a hydraulic hoist 2 for driving the working gate body 3 to rise and fall; a counterweight 4, disposed on the working gate body 3, for adjusting the total weight of the working gate body 3 and the balance of the left and right counterweights, so that the total weight of the working gate body 3 is greater than the maximum frictional force it experiences during descent; a sealing assembly, disposed on the working gate body 3, for forming a seal between the working gate body 3 and the gate slot 1; a pressure balancing unit 5, including a gap drain pipe 51, a navigation channel drain pipe 52, a gap drain valve group 53, a new drain valve group 54, a navigation channel drain valve group 55, and a control system; the working gate body 3, when subjected to... The connection point is aligned with the upstream reclining door 6 of the ship-bearing chamber, forming a gap water cavity 56 between them; one end of the gap drainage pipe 51 is connected to the gap water cavity 56, and the other end is connected to the downstream vertical shaft; one end of the navigation channel drainage pipe 52 is connected to the upstream pilot channel, and the other end is connected to the middle of the gap drainage pipe 51; the gap drainage valve group 53 is located at the end of the gap drainage pipe 51 near the gap water cavity 56; the newly added drainage valve group 54 is located at the end of the gap drainage pipe 51 near the downstream vertical shaft; and the navigation channel drainage valve group 55 is located on the navigation channel drainage pipe 52; the control system is used to control the opening and closing of each valve group, so as to introduce water from the upstream pilot channel into the gap water cavity 56 before opening the working small door body 3, thereby balancing the water pressure difference between the upstream and downstream sides of the working small door body 3.

[0025] This embodiment provides an anti-jamming system for the working gate of a hydraulic ship lift. Through the comprehensive setting of the counterweight 4, the sealing components, and the pressure balancing unit 5, the system can effectively solve the problem of jamming caused by excessive frictional resistance due to upstream water pressure, thereby reducing the equipment failure rate.

[0026] The anti-jamming system for the working gate of the hydraulic ship lift includes a gate slot 1, a working gate body 3, a hydraulic hoist 2, a counterweight 4, a sealing assembly, and a pressure balancing unit 5. The gate slot 1 is located at the concave notch of the upper gate's working gate, extending vertically to provide a guide rail for the lifting and lowering of the working gate body 3. The working gate body 3 is a planar sliding structure with gate leaf dimensions of 13.00m (width) × 3.70m (height), slidably installed within the gate slot 1, and capable of vertical movement. The hydraulic hoist 2 is a double-cylinder plunger type hoist, driven and connected to the working gate body 3, used to control the lifting and lowering of the working gate body 3. The working gate body 3 descends under its own weight, and the hydraulic hoist 2 controls the descent speed during the descent process.

[0027] The counterweight 4 is fixedly installed on the working gate body 3. In a specific example, the counterweight 4 is distributed on the left and right sides. By adjusting the total weight of the counterweight 4 and the weight distribution on the left and right sides, the total weight of the working gate body 3 is made greater than the maximum sliding friction force it experiences during descent. The maximum sliding friction force experienced by the working gate body 3 during descent originates from the product of the normal pressure generated by the upstream water pressure and the coefficient of friction. When the total weight of the working gate body 3 exceeds this maximum sliding friction force, the working gate body 3 can descend stably by its own weight, avoiding jamming or stalling due to friction exceeding its own weight.

[0028] The sealing assembly is located between the working door body 3 and the door groove 1 to form a reliable seal between the two and prevent water in the gap water cavity 56 from leaking outward.

[0029] The pressure balancing unit 5 is used to balance the water pressure difference between the upstream and downstream sides of the working gate body 3 before it is opened. When the working gate body 3 is in the docking position, it forms a gap water cavity 56 with the upstream horizontal door 6 of the ship-carrying compartment. The pressure balancing unit 5 includes a gap drain pipe 51, a navigation channel drain pipe 52, a gap drain valve group 53, a new drain valve group 54, a navigation channel drain valve group 55, and a control system.

[0030] The gap drain pipe 51 is arranged vertically, with one end connected to the gap water cavity 56 and the other end extending downwards to the downstream shaft. One end of the navigation channel drain pipe 52 is connected to the upstream navigation channel, and the other end intersects and connects to the middle of the gap drain pipe 51. A gap drain valve assembly 53 is installed on the gap drain pipe 51 near the gap water cavity 56 to control the on / off state of the gap drain pipe 51 at that end. A newly added drain valve assembly 54 is installed on the gap drain pipe 51 near the downstream shaft to control the on / off state of the gap drain pipe 51 at that end. A navigation channel drain valve assembly 55 is installed on the navigation channel drain pipe 52 to control the on / off state of the navigation channel drain pipe 52.

[0031] The control system is electrically connected to the gap drain valve group 53, the newly added drain valve group 54, the navigation channel drain valve group 55, and the hydraulic gate hoist 2. The control system is used to control the opening and closing actions of each valve group according to the preset control logic or the instructions of the host computer, so that before opening the working gate body 3, the water in the upstream navigation channel is introduced into the gap water chamber 56 through the navigation channel drain pipe 52 and the gap drain pipe 51, so that the water pressure in the gap water chamber 56 is nearly balanced with the water pressure in the upstream navigation channel.

[0032] In another embodiment, the control system is also a host computer sequential control system, which enables remote automatic control by issuing commands from the host computer. Regarding input signals, the fully open, fully closed, and over-torque signals of each valve group are input to the control system via digital input (DI) modules. Regarding output control, the opening and closing control commands for each valve group are issued via digital output (DO) modules to control the operation of each valve group. The control system also includes a newly added digital input module for receiving signals from the newly added drain valve group 54.

[0033] In a specific example, to ensure the timeliness of the operation, the signal feedback delay is no more than 1 second and the fault alarm response time is no more than 2 seconds.

[0034] In some embodiments, the control system is configured to respond to the pressurization command from the host computer and perform a pressure balancing operation according to a preset linkage sequence: first, control the newly added drain valve group 54 to close to cut off the connection between the gap water chamber 56 and the downstream vertical shaft; after it is closed, automatically control the navigation channel drain valve group 55 to open, so that the water from the upstream navigation channel enters the gap water chamber 56 in sequence through the navigation channel drain pipe 52 and the gap drain pipe 51; after the pressurization delay meets the set time, automatically control the navigation channel drain valve group 55 and the gap drain valve group 53 to close to isolate and seal the gap water chamber 56 after pressurization balancing.

[0035] This embodiment defines the pressure balancing operation sequence of the control system, realizing automated linkage control of the charging and pressurizing process. It eliminates the need for manual operation of each valve, effectively improving operational efficiency and reducing safety risks.

[0036] Specifically, the control system is configured to respond to the pressurization command issued by the host computer and automatically execute the following pressure balancing operations according to the preset linkage sequence.

[0037] The first step is for the control system to close the newly added drain valve assembly 54. When the newly added drain valve assembly 54 is fully open, the gap water chamber 56 is connected to the downstream shaft via the gap drain pipe 51, making it impossible to maintain water pressure. After the control system issues a closing command, the two electric valves in the newly added drain valve assembly 54 close sequentially or simultaneously, cutting off the connection between the gap water chamber 56 and the downstream shaft. The control system continuously monitors the position feedback signal of the newly added drain valve assembly 54 until it is confirmed that it has reached the fully closed position.

[0038] The second step involves the control system automatically opening the navigation channel drainage valve assembly 55 after confirming that the newly added drainage valve assembly 54 is fully closed. Initially, the navigation channel drainage valve assembly 55 is fully closed, isolating the upstream navigation channel from the gap drainage pipe 51. After the control system issues an opening command, the two electric valves in the navigation channel drainage valve assembly 55 open sequentially or simultaneously. At this time, water from the upstream navigation channel flows into the navigation channel drainage pipe 52 under water pressure, then enters the gap drainage pipe 51 at the confluence point, and finally enters the gap water chamber 56. Throughout this process, the gap drainage valve assembly 53 remains fully open to ensure unobstructed water flow.

[0039] Thirdly, after the pressurization delay meets the set time, the control system automatically closes the channel drain valve assembly 55 and the gap drain valve assembly 53. During the water filling process, the control system continuously times the water. When the water filling time reaches the preset set time (e.g., 240 seconds), it determines that the water pressure in the gap water chamber 56 has reached equilibrium with the water pressure in the upstream navigation channel. The control system first closes the channel drain valve assembly 55 to prevent water from flowing into the upstream navigation channel, and then closes the gap drain valve assembly 53 to isolate the gap water chamber 56 from the gap drain pipe 51. At this point, the gap water chamber 56 is completely sealed, and the water pressure inside the chamber remains balanced with the water pressure in the upstream navigation channel.

[0040] During the above control process, the newly added drain valve group 54 remains closed until the pressure charging is completed and it will only reopen when needed. Through the above preset linkage sequence, the operator only needs to send a pressure charging command once to automatically complete the entire pressure charging process without having to manually operate the valves on-site.

[0041] In some embodiments, after the water pressure in the gap water cavity 56 is balanced with the water pressure in the upstream navigation channel, the control system controls the hydraulic gate hoist 2 to drive the working gate body 3 to descend.

[0042] Specifically, after the above-mentioned leveling and pressure-pressurizing operation is completed, the gap water cavity 56 is sealed and the water pressure inside the cavity is in equilibrium with the water pressure in the upstream navigation channel. At this time, the water pressure on the upstream side of the working gate body 3 is basically equal to the water pressure on the downstream side, and the unbalanced water pressure acting on the working gate body 3 is significantly reduced, thereby greatly reducing the friction between the working gate body 3 and the gate slot 1.

[0043] After confirming that the water pressure in the gap water chamber 56 has reached equilibrium, the control system sends a descent command to the hydraulic gate hoist 2. Responding to this command, the hydraulic gate hoist 2 releases the holding force on the working gate body 3, allowing it to descend smoothly along the gate groove 1 under its own weight. Since the water pressure on the upstream and downstream sides of the working gate body 3 is now nearly balanced, the lateral water pressure acting on the gate body is significantly reduced, and the frictional force decreases accordingly. The working gate body 3 can overcome frictional resistance and descend smoothly without jamming.

[0044] During the descent, the hydraulic circuit in the hydraulic gate hoist 2 regulates and controls the descent speed to ensure that the working gate body 3 descends smoothly to the target position at a controllable speed. The control system monitors the position signal of the working gate body 3 in real time. When the working gate body 3 descends to the correct position, the control system issues a stop command to complete the docking operation.

[0045] In a specific example, after the pressurization delay ends and the trough drain valve group 55 and the gap drain valve group 53 are closed, the control system adds a short safety waiting interval (e.g., 2 to 5 seconds) to ensure that the water flow in the gap water chamber 56 is completely stable before controlling the working gate body 3 to descend.

[0046] In some embodiments, the control system is further configured to respond to a water discharge command from the host computer by controlling the opening of the gap drain valve group 53 and the additional drain valve group 54 to discharge the water in the gap water chamber 56 to the downstream vertical shaft through the gap drain pipe 51.

[0047] When the ship lift needs to disconnect after completing the upstream docking operation, the water in the gap water chamber 56 must be drained. The control system is configured to respond to the water discharge command from the host computer and automatically execute the water discharge operation.

[0048] Specifically, operators send a water discharge command (e.g., "open gap water valve") via a host computer. Upon receiving this command, the control system opens the gap water discharge valve group 53 and the newly added drain valve group 54. When gap water discharge valve group 53 opens, water in the gap water chamber 56 can flow into the gap water discharge pipeline 51; when the newly added drain valve group 54 opens, the channel between the gap water discharge pipeline 51 and the downstream shaft is connected. Under gravity, the water in the gap water chamber 56 flows sequentially through the gap water discharge pipeline 51 and the downstream shaft, ultimately being discharged downstream.

[0049] During the water discharge process, the channel discharge valve assembly 55 remains closed to prevent water from flowing back into the upstream navigation channel. The control system continuously monitors the opening and closing status of each valve assembly. When both the gap discharge valve assembly 53 and the newly added discharge valve assembly 54 are fully open, the discharge channel is completely unobstructed, and water in the gap water chamber 56 is continuously discharged until the water level in the gap water chamber 56 drops to its minimum.

[0050] In one specific implementation, after confirming that the water discharge is complete, the control system can automatically close the gap drain valve group 53 and the newly added drain valve group 54, restoring the pressure balancing unit 5 to its initial state. In the initial state, the gap drain valve group 53 and the newly added drain valve group 54 are in the fully open position, and the navigable tank drain valve group 55 is in the fully closed position, preparing for the next filling and pressurization operation.

[0051] In some embodiments, the increase in the counterweight 4 is calculated based on the maximum sliding friction force determined by the product of the maximum water pressure and the coefficient of friction on the working gate body 3, and the original total weight of the working gate body 3. The increase in the counterweight is not less than the difference between the maximum sliding friction force and the original total weight.

[0052] The process for determining the increase in counterweight is as follows. First, calculate the maximum water pressure on the main body 3 of the working gate during its descent. Establish a coordinate system with the top of the main body 3 as the origin, moving downwards along the height direction. Take an area element dS at coordinate y, then dS = W × dy, where W is the width of the main body 3. The water pressure on this area element is dF = ρ × g × h × dS, where ρ is the density of water, g is the acceleration due to gravity, and h is the water depth. Integrate over the entire height of the main body 3 to obtain the total water pressure F on the main body 3.

[0053] After obtaining the total water pressure, multiply it by the coefficient of friction μ to obtain the maximum sliding friction force F_friction = μ × F experienced by the working gate body 3 when it descends. The coefficient of friction μ is determined based on the friction pair material and lubrication condition between the working gate body 3 and the gate groove 1. In one example, for a planar sliding working gate, the coefficient of friction μ is taken as 0.3.

[0054] Let the original total weight of the working door body 3 be Goriginal (including the designed weight of the door leaf, the weight of the original counterweight 4, etc.). To enable the working door body 3 to overcome the decrease in sliding friction due to its own weight, the total weight of the working door body 3 needs to be greater than the maximum sliding friction, i.e., Goriginal + ΔG > Ffriction, where ΔG is the required increase in counterweight weight. Therefore, the increase in counterweight ΔG should not be less than Ffriction - Goriginal.

[0055] In one specific embodiment, the working gate body 3 has a width W of 13.00m and a height H of 3.70m. Its original total weight G was 26.08t (including the gate leaf design weight of 17.68t, the 8.1t counterweight used during the construction of the ship lift, and the 0.3t commissioning counterweight). Calculations show that the maximum water pressure F_water_pressure experienced by the working gate body 3 is approximately 872kN (equivalent to approximately 88.98t), and the maximum sliding friction F_friction is approximately 26.69t. Therefore, the original total weight G is slightly less than the maximum sliding friction F_friction, requiring an additional counterweight of at least 0.61t. Considering factors such as the load-bearing capacity of the hydraulic pipelines and components, and the balance of the left and right counterweights, the actual increase in counterweight is 0.875t. The left and right counterweights are adjusted according to actual measurement deviations.

[0056] The increase in counterweight determined by the above calculations ensures that the total weight of the working gate body 3 is always greater than the sliding friction force at any moment during the descent process, thereby ensuring that the working gate body 3 can descend smoothly by its own weight.

[0057] In some embodiments, the door groove 1 is a cleaned door groove 1 after cleaning treatment, and there are no visible particles with a diameter ≥1cm remaining in the cleaned door groove 1.

[0058] Specifically, before installing the working door body 3 or during maintenance, the working door body 3 is lifted off the door slot 1, and the interior of the door slot 1 is thoroughly cleaned. Cleaning includes removing sediment, debris, and foreign objects from the bottom and side walls of the door slot 1. In one example, a crane is used to suspend the working door body 3 above the door slot 1, fully exposing the door slot 1. A high-pressure water gun with a working pressure of 20 MPa is used to flush the inner walls and bottom of the door slot 1, effectively removing attached mud and impurities. For residual debris that is difficult to remove with the high-pressure water gun, manual cleaning is used as a supplement.

[0059] After cleaning, a visual inspection of the inside of door slot 1 is conducted. The standard for cleaning door slot 1 is: there are no visible particles with a diameter greater than or equal to 1 cm remaining in door slot 1, nor are there any large debris such as tree branches or plastic bags remaining. After cleaning, door slot 1 ensures that the working door body 3 will not get stuck due to debris during the lifting and lowering process. It also facilitates a reliable fit between the sealing components and door slot 1, improving the sealing effect.

[0060] In some embodiments, the gap drain valve group 53, the additional drain valve group 54, and the navigation channel drain valve group 55 are each composed of two electric valves connected in series.

[0061] Specifically, each valve assembly consists of two electric valves connected in series. "Connected in series" means that the two electric valves are installed sequentially along the pipeline, and water must pass through both valves in turn before flowing through that section of the pipeline. Taking the gap drain valve assembly 53 as an example, two electric valves are installed sequentially along the water flow direction at the end of the gap drain pipeline 51 near the gap water chamber 56. Similarly, the newly added drain valve assembly 54 and the trough drain valve also consist of two solenoid valves connected in series.

[0062] The structure of two electric valves connected in series has the following advantages. First, during operation, even if one electric valve malfunctions (such as failing to close or open normally), the other electric valve can still perform the switching operation, ensuring reliable connection and disconnection of the pipeline and improving the system's fault tolerance. Second, during maintenance, one electric valve can be closed first to isolate the pipeline before the other electric valve can be repaired or replaced, without completely draining the water from the pipeline, thus reducing maintenance difficulty.

[0063] Each electric valve is equipped with a position feedback signal output, including a fully open signal, a fully closed signal, and an over-torque signal. These signals are connected to the digital input module of the control system, allowing the control system to monitor the operating status of each electric valve in real time. The actuator of the electric valve is connected to the control system via a control cable, and the control system sends valve opening and closing commands through the digital output module.

[0064] In some embodiments, the sealing assembly includes a side water seal and a bottom water seal, wherein the compression of the side water seal to the corresponding water seal seat is 2 mm to 4 mm, and the compression of the bottom water seal to the corresponding water seal seat is 6 mm to 10 mm.

[0065] The sealing assembly includes a side water seal and a bottom water seal. The side water seals are installed on both sides of the working gate body 3 (i.e., the left bank side and the right bank side) to form a seal between the sides of the working gate body 3 and the gate slot 1. The bottom water seal is installed at the bottom of the working gate body 3 to form a seal between the bottom of the working gate body 3 and the bottom surface of the gate slot 1. Both the side and bottom water seals are made of rubber, and their material and hardness comply with the relevant national standards for gate water seals.

[0066] The compression amount between the side water seal and the corresponding water seal seat on the side wall of the door slot 1 is set to 2mm to 4mm. When the compression amount is within this range, the side water seal can form an effective contact seal with the side wall of the door slot 1, preventing water in the gap water cavity 56 from leaking from the side. At the same time, the frictional resistance generated by the elastic deformation within this compression range is small and will not significantly increase the resistance when the working door body 3 descends.

[0067] The compression between the bottom water seal and the corresponding water seal seat at the bottom of the door groove 1 is set to 6mm to 10mm. After the working door body 3 descends into position, the bottom water seal withstands significant water pressure, requiring a large compression to form a reliable seal. A bottom water seal within this compression range can effectively prevent water leakage from the bottom. If the bottom water seal compression is insufficient, replace it with a new water seal that meets the requirements.

[0068] In some embodiments, the sealing assembly further includes a guide wheel pad disposed between the working door body 3 and the guide wheel.

[0069] Specifically, a guide wheel pad is provided between the working door body 3 and the guide wheel. The guide wheel is installed on the guide rail of the door groove 1 and is used to guide the working door body 3 to slide up and down along the door groove 1. The guide wheel pad is a gasket structure and is installed between the mounting contact surfaces of the working door body 3 and the guide wheel.

[0070] By adjusting the thickness of the guide wheel pad, the position of the working gate body 3 relative to the gate slot 1 can be changed, thereby indirectly adjusting the compression between the side water seal and the corresponding water seal seat. Specifically, when it is necessary to increase the compression of the side water seal, a guide wheel pad of appropriate thickness can be added between the working gate body 3 and the guide wheel, causing the working gate body 3 to move closer to the side wall of the gate slot 1, thereby increasing the compression between the side water seal and the side wall of the gate slot 1. Conversely, when it is necessary to decrease the compression of the side water seal, the thickness of the guide wheel pad can be reduced.

[0071] After the side water seal is re-ground, the thickness of the water seal may be reduced, which may require corresponding adjustment of the guide wheel gasket thickness to compensate and maintain the compression of the side water seal within the range of 2mm to 4mm. The guide wheel gasket is made of corrosion-resistant stainless steel and has sufficient mechanical strength and dimensional stability.

[0072] In some embodiments, the set time is 240 seconds; the control system is a host computer sequential control system, which is used to realize remote "one-click pressurization" control. The host computer sequential control system has the function of collecting valve position feedback signals, and its signal feedback delay is ≤1 second and the fault alarm response time is ≤2 seconds.

[0073] This embodiment defines the setting time of the pressurization delay and the type and performance parameters of the control system.

[0074] The set time is specifically 240 seconds. This set time is determined based on a combination of parameters, including the volume of the gap water cavity 56, the diameters of the channel drain pipes 52 and 51, and the water pressure in the upstream approach channel. Within this time, the water in the upstream approach channel will completely fill the gap water cavity 56, and the water pressure in the gap water cavity 56 will reach equilibrium with the water pressure in the upstream approach channel. In another embodiment, the set time can be adjusted according to actual operating conditions. For example, when the upstream water level changes or the pipe diameter is adjusted, the set time can be increased or decreased accordingly to ensure the filling and pressure-boosting effect.

[0075] The control system is a host computer sequential control system. Operators click the "One-Click Pressurization" button or send the "Close Gap Water Valve" command on the host computer interface in the central control room, and the host computer sequential control system automatically completes the entire pressure balancing operation process according to the preset program. This sequential control process includes: closing the newly added drain valve group 54 → opening the navigation channel drain valve group 55 → delaying for 240 seconds → closing the navigation channel drain valve group 55 and the gap drain valve group 53 → opening the newly added drain valve group 54. All actions require no manual intervention, realizing remote automatic control of the entire pressurization and leveling process.

[0076] The host computer sequential control system has a valve position feedback signal acquisition function. The fully open, fully closed, and over-torque signals of each electric valve are acquired and sent to the control system via a digital input module. After issuing a control command, the system monitors the feedback signal in real time to confirm whether each valve has performed its intended action. If no corresponding position signal is received within the specified feedback delay time after a control command is issued, the system determines that the valve's action is abnormal and triggers a fault alarm.

[0077] Regarding the performance parameters of the host computer sequential control system, the signal feedback delay is no more than 1 second, meaning the time interval from the valve actually reaching its position to the control system receiving the position signal does not exceed 1 second, ensuring the system can promptly obtain the valve's true status. The fault alarm response time is no more than 2 seconds, meaning the time from detecting an abnormal valve status to the host computer interface displaying alarm information does not exceed 2 seconds, ensuring operators can promptly be aware of abnormal situations and take appropriate measures.

[0078] With the automatic control of the host computer sequential control system, operators can complete the leveling and pressurization operation without leaving the central control room, eliminating the safety risks of working near the edge and in the air, and greatly improving the efficiency of operation, reducing the leveling and pressurization time from 20 minutes required for manual operation to less than 8 minutes.

[0079] In the description of this invention, it should be understood that the terms "center," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," "counterclockwise," "axial," "radial," and "circumferential" indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are used only for the convenience of describing this invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this invention.

[0080] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one of that feature. In the description of this invention, "a plurality of" means at least two, such as two, three, etc., unless otherwise explicitly specified.

[0081] In this invention, unless otherwise explicitly specified and limited, the terms "installation," "connection," "linking," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection, an electrical connection, or a connection that allows communication between them; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components, unless otherwise explicitly limited. Those skilled in the art can understand the specific meaning of the above terms in this invention according to the specific circumstances.

[0082] In this invention, unless otherwise explicitly specified and limited, "above" or "below" the second feature can mean that the first feature is in direct contact with the second feature, or that the first feature is in indirect contact with the second feature through an intermediate medium. Furthermore, "above," "over," and "on top" of the second feature can mean that the first feature is directly above or diagonally above the second feature, or simply that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature can mean that the first feature is directly below or diagonally below the second feature, or simply that the first feature is at a lower horizontal level than the second feature.

[0083] In this invention, the terms "one embodiment," "some embodiments," "example," "specific example," or "some examples," etc., refer to a specific feature, structure, material, or characteristic described in connection with that embodiment or example, which is included in at least one embodiment or example of the invention. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples. Moreover, without contradiction, those skilled in the art can combine and integrate the different embodiments or examples described in this specification, as well as the features of different embodiments or examples.

[0084] Although the above embodiments have been shown and described, it is understood that the above embodiments are exemplary and should not be construed as limiting the present invention. Any changes, modifications, substitutions and variations made to the above embodiments by those skilled in the art are within the protection scope of the present invention.

Claims

1. A system for preventing jamming of the working gate of a hydraulic ship lift, characterized in that, include: The door slot, the working door body slidably disposed in the door slot, and the hydraulic opening and closing mechanism for driving the working door body to rise and fall; A counterweight is provided on the working door body to adjust the total weight of the working door body and the balance of the left and right counterweights, so that the total weight of the working door body is greater than the maximum frictional force it experiences during its descent. A sealing assembly is provided on the working door body and is used to form a seal between the working door body and the door groove; The pressure balancing unit includes a gap drain pipe, a channel drain pipe, a gap drain valve assembly, a new drain valve assembly, a channel drain valve assembly, and a control system. The working small door body is connected to the upstream horizontal door of the ship-bearing chamber at the docking position, forming a gap water cavity between them. One end of the gap drain pipe is connected to the gap water cavity, and the other end is connected to the downstream vertical shaft. One end of the channel drain pipe is connected to the upstream pilot channel, and the other end is connected to the middle of the gap drain pipe. The gap drain valve assembly is located at the end of the gap drain pipe near the gap water cavity. The new drain valve assembly is located at the end of the gap drain pipe near the downstream vertical shaft. The channel drain valve assembly is located on the channel drain pipe. The control system is used to control the opening and closing of each valve group so as to introduce water from the upstream navigation channel into the gap water cavity before opening the working gate body, thereby balancing the water pressure difference between the upstream and downstream sides of the working gate body.

2. The anti-jamming system for the working gate of the hydraulic ship lift according to claim 1, characterized in that, The control system is configured to respond to the pressurization command from the host computer and perform pressure balancing operations according to a preset linkage sequence: first, control the newly added drain valve group to close to cut off the connection between the gap water chamber and the downstream vertical shaft; after it is closed, automatically control the navigation channel drain valve group to open, so that the water from the upstream navigation channel enters the gap water chamber through the navigation channel drain pipe and the gap drain pipe in sequence; after the pressurization delay meets the set time, automatically control the navigation channel drain valve group and the gap drain valve group to close to isolate and seal the gap water chamber after pressurization balancing.

3. The anti-jamming system for the working gate of the hydraulic ship lift according to claim 2, characterized in that, After the water pressure in the gap water cavity is balanced with the water pressure in the upstream navigation channel, the control system controls the hydraulic gate hoist to drive the working gate body to descend.

4. The anti-jamming system for the working gate of the hydraulic ship lift according to claim 3, characterized in that, The control system is also configured to respond to the water discharge command from the host computer and control the opening of the gap drain valve group and the newly added drain valve group to discharge the water in the gap water chamber to the downstream vertical shaft through the gap drain pipeline.

5. The anti-jamming system for the working gate of the hydraulic ship lift according to claim 1, characterized in that, The increase in the counterweight is calculated based on the maximum sliding friction force determined by the product of the maximum water pressure and the coefficient of friction on the working gate body, and the original total weight of the working gate body. The increase in the counterweight is not less than the difference between the maximum sliding friction force and the original total weight.

6. The anti-jamming system for the working gate of the hydraulic ship lift according to claim 1, characterized in that, The door groove is a cleaned door groove that has undergone cleaning treatment, and there are no visible particles with a diameter of ≥1cm remaining in the cleaned door groove.

7. The anti-jamming system for the working gate of the hydraulic ship lift according to claim 1, characterized in that, The gap drain valve group, the newly added drain valve group, and the navigation channel drain valve group are all composed of two electric valves connected in series.

8. The anti-jamming system for the working gate of the hydraulic ship lift according to claim 1, characterized in that, The sealing assembly includes a side water seal and a bottom water seal. The compression of the side water seal with the corresponding water seal seat is 2mm to 4mm, and the compression of the bottom water seal with the corresponding water seal seat is 6mm to 10mm.

9. The anti-jamming system for the working gate of the hydraulic ship lift according to claim 8, characterized in that, The sealing assembly also includes a guide wheel pad disposed between the working door body and the guide wheel.

10. The anti-jamming system for the working gate of the hydraulic ship lift according to claim 2, characterized in that, The set time is 240 seconds; the control system is a host computer sequential control system, which is used to realize remote "one-click pressurization" control. The host computer sequential control system has the function of collecting valve position feedback signals, and its signal feedback delay is ≤1 second and the fault alarm response time is ≤2 seconds.

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