An emergency braking checking method and system for a full-balanced steel wire rope hoist type ship lift

Abstract

The present application relates to the technical field of ship lift in hydraulic engineering, and particularly relates to a full-balanced steel wire rope hoist type ship lift emergency braking checking method and system. In view of the problems that the existing checking method is not adapted to the full-balanced steel wire rope hoist type balanced friction drum characteristics, the working condition coverage is not complete, and the checking dimension is single, the present application provides a full-working condition and multi-dimension integrated checking method. The method comprises the following steps: respectively calculating the system equivalent mass and unbalanced load under normal lifting and water leakage empty working conditions; calculating the system translational acceleration under each working condition based on the braking system parameters; selecting the maximum acceleration to calculate the impact load coefficient; and on this basis, checking the strength and anti-skid of the steel wire rope. The present application realizes the linkage checking of the load, acceleration, impact coefficient and steel wire rope performance of the full-balanced steel wire rope hoist type ship lift in the emergency braking process, significantly improves the comprehensiveness, accuracy and engineering applicability of the checking, and provides reliable support for the safety design of the ship lift.

Description

Technical Field

[0001] This invention relates to the field of ship lift technology in water conservancy projects, specifically a method and system for verifying the emergency braking of a fully balanced wire rope winch ship lift. Background Technology

[0002] Fully balanced wire rope winch-type vertical ship lifts have been widely used in large-scale hydraulic ship lift projects due to their advantages such as good economy and low energy consumption. The introduction of balanced friction drums has solved the problem of preventing water leakage accidents, improving the safety and engineering applicability of fully balanced wire rope winch-type vertical ship lifts. However, the operating conditions of ship lifts are complex. During normal lifting and lowering of the ship chamber, it needs to bear the combined load of the ship and the water. Under water leakage conditions, it faces the risk of sudden load changes and system imbalance. The impact load and wire rope slippage problem in emergency braking scenarios have become the core hidden dangers restricting system safety.

[0003] Existing verification methods for emergency braking systems have many limitations: On the one hand, traditional methods are mostly based on ordinary drum structure designs, which do not fully adapt to the friction force transmission characteristics of balanced friction drums and ignore their special characteristics in load balance adjustment and anti-slip performance; on the other hand, existing technologies often do not achieve full coverage of working conditions, and the calculation of the equivalent mass and unbalanced load of the system under extreme working conditions such as water leakage and air leakage is not accurate enough. Furthermore, no linkage verification mechanism between the impact load coefficient and the strength and anti-slip performance of the wire rope has been established, making it difficult to fully guarantee the system safety during emergency braking.

[0004] As ship lifts become larger and more sophisticated, the weight of the ship compartments, the lifting height, and the navigable tonnage continue to increase, placing higher demands on the accuracy of emergency braking system verification. Existing technologies can no longer meet the safety verification requirements of balanced friction drum-type fully balanced ship lifts. There is an urgent need for a comprehensive verification method that accurately adapts to its structural characteristics and operational features, enabling integrated and precise verification of system load, acceleration, impact coefficient, and wire rope performance under emergency braking scenarios, thus providing technical support for ship lift design. Summary of the Invention

[0005] This invention provides a method and system for verifying the emergency braking of a fully balanced wire rope winch-type ship lift, enabling integrated and accurate verification of system load, acceleration, impact coefficient, and wire rope performance under emergency braking scenarios, providing technical support for ship lift design.

[0006] A method for verifying the emergency braking of a fully balanced wire rope winch-type ship lift includes the following steps:

[0007] Based on the operating characteristics of a fully balanced wire rope winch-type vertical ship lift, the total equivalent mass M of the system under normal lifting conditions of the ship compartment is calculated. t1 The total equivalent mass M of the system under water leakage conditions t2And calculate the unbalanced load on both sides of the drum under normal lifting conditions of the ship's cabin. Unbalanced load F on both sides of the drum under water leakage conditions u2 ;

[0008] Based on the total equivalent mass M of the system under normal lifting and lowering conditions of the ship's compartment t1 Unbalanced loads on both sides of the drum and the total equivalent mass M of the system under the condition of water leakage. t2 Unbalanced load F on both sides of the drum u2 In addition, the performance and parameters of the ship lift's safety braking system were determined, and the translational acceleration of the system during normal lifting and lowering of the ship compartment was calculated. The translational acceleration α of the system under the condition of water leakage w2 ;

[0009] Select the translational acceleration of the system during normal lifting and lowering of the ship's cabin. The translational acceleration α of the system under the condition of water leakage w2 The maximum value in, combined with the dynamic load factor φ d Calculate the impact load factor K of the system. d ;

[0010] Based on the system's impact load coefficient K d Breaking tensile force T of steel wire rope s The number of wire ropes n2 and the safety factor k of the wire rope s Verify whether the strength of the steel wire rope under impact load meets the requirements;

[0011] Based on the system's impact load coefficient K d counterweight M p Design water depth and water body weight (M) w Gravity balance weight M z Check whether there is slippage between the wire rope and the balance friction drum.

[0012] Furthermore, based on the operating characteristics of the fully balanced wire rope winch-type vertical ship lift, the total equivalent mass M of the system under normal lifting conditions of the ship compartment is calculated. t1 The total equivalent mass M of the system under water leakage conditions t2 Specifically, this includes: the total equivalent mass M of the system under normal lifting and lowering conditions of the ship's cabin. t1 According to formula (1), the total equivalent mass M of the system under the water leakage condition is calculated. t2 Calculate according to formula (2):

[0013] (1);

[0014] (2);

[0015] In the formula, M t1 M is the total equivalent mass of the system under normal lifting and lowering conditions of the ship's cabin; t2 The total equivalent mass of the system under the condition of water leakage in the ship compartment; h is the water depth inside the compartment; L is the length of the ship compartment; ∆h is the depth of water during misloading; M w For the design water depth and water body weight; M s M represents the weight of the ship's compartment. p Total weight for counterweight; J d1 J represents the total rotational inertia of the main hoisting system without considering the balancing friction drum; d2 To account for the total rotational inertia of the main hoisting system of the balancing friction drum; r d Where is the radius of the roll.

[0016] Furthermore, based on the operating characteristics of the fully balanced wire rope winch-type vertical ship lift, the unbalanced loads on both sides of the drum under normal lifting conditions of the ship compartment are calculated. Unbalanced load F on both sides of the drum under water leakage conditions u2 Specifically, this includes: calculating the unbalanced load on both sides of the drum during normal lifting and lowering of the ship compartment according to formula (3). ; Calculate the unbalanced load F on both sides of the drum under the water leakage condition of the ship chamber according to formula (4). u2 :

[0017] (3);

[0018] (4);

[0019] In the formula, F u1 This refers to the unbalanced load on both sides of the drum during normal lifting and lowering of the ship's compartment; F u2 The unbalanced load on both sides of the drum under the condition of water leakage in the ship chamber; F k The unbalanced load is caused by factors such as system inertia, frictional resistance, wire rope stiffness resistance, and wind pressure; g is the acceleration due to gravity; h is the water depth inside the compartment; L is the length of the compartment; ∆h is the depth of the misloaded water; M w For the design water depth and water body weight; M s M represents the weight of the ship's compartment. p To balance the total weight.

[0020] Furthermore, the safety braking system of the fully balanced wire rope winch vertical ship lift implements emergency braking by engaging the safety brake on the lifting drum brake disc during normal lifting and lowering of the ship compartment; when the ship compartment experiences water leakage, emergency braking is implemented by engaging the safety brake on both the lifting drum brake disc and the balance friction drum brake disc.

[0021] Furthermore, when the ship's cabin is in normal lifting and lowering and emergency braking is applied, the translational acceleration of the system is calculated according to formula (5). :

[0022] (5);

[0023] In the formula, α w1 The translational acceleration of the system when applying emergency braking for normal raising and lowering of the ship's cabin; F s1 To increase the clamping force of a single brake head in the drum safety brake; s1 To increase the number of brake heads in the drum safety brake; μ s η is the coefficient of friction between the brake head and the brake disc. s For the efficiency of the safety brake; r s F is the braking radius; u1 This refers to the unbalanced load on both sides of the drum during normal lifting and lowering of the ship's compartment; M t1 The total equivalent mass of the system under normal lifting and lowering conditions of the ship's compartment.

[0024] Furthermore, when emergency braking is performed under the condition of water leakage in the ship compartment, the translational acceleration α of the system is calculated according to formula (6). w2 :

[0025] (6);

[0026] In the formula, α w2 F is the translational acceleration of the system when emergency braking is applied under conditions of water leakage in the ship's compartment; s2 To balance the clamping force of a single brake head in the friction drum safety brake; n s1 To balance the number of brake heads in the friction drum safety brake; F u2 The unbalanced load on both sides of the drum under the condition of water leakage in the ship chamber; M t2 The total equivalent mass of the system under the condition of water leakage in the ship compartment.

[0027] Furthermore, the translational acceleration of the system during the normal lifting and lowering of the ship's compartment was selected. The translational acceleration α of the system under the condition of water leakage w2 The maximum value in, combined with the dynamic load factor φ d Calculate the impact load factor K of the system. d Specifically, this includes calculating the impact load coefficient K of the system according to equation (7). d :

[0028] (7);

[0029] In the formula, K d α is the impact load factor of the system. max φ is the translational acceleration of the maximum system. d The dynamic load factor for emergency stop, unexpected stop, and non-continuous braking is set to 3.

[0030] Furthermore, based on the system's impact load factor K d Breaking tensile force T of steel wire rope s The number of wire ropes n2 and the safety factor k of the wire rope s The strength of the wire rope under impact load is checked to ensure it meets the requirements. Specifically, the maximum tension of the wire rope under impact load should meet the requirements of equation (8).

[0031] (8);

[0032] In the formula, T s n is the breaking tensile strength of the wire rope; n2 is the number of wire ropes; k s The safety factor for the wire rope is taken as 7; h is the water depth inside the compartment; L is the length of the compartment; ∆h is the depth of water where the ship is overloaded; M w The design depth is the weight of the water body; g is the acceleration due to gravity; α w1 The translational acceleration of the system when applying emergency braking for normal raising and lowering of the ship's cabin; α w2 M is the translational acceleration of the system when emergency braking is applied under conditions of water leakage in the ship's compartment; s M represents the weight of the ship's compartment. p To balance the total weight.

[0033] Furthermore, based on the system's impact load factor K d counterweight M p Design water depth and water body weight (M) w Gravity balance weight M z To check whether there is slippage between the wire rope and the friction balance drum, specifically including: under impact load conditions, when equation (9) holds, there is no slippage between the wire rope and the friction balance drum:

[0034] (9);

[0035] In the formula, M p To balance the weight; M w For the design water depth and water body weight; M z The equilibrium mass is the weight under gravity; g is the acceleration due to gravity; K d α is the impact load factor of the system. w2 n1 is the translational acceleration of the system when emergency braking is performed under the condition of water leakage in the ship chamber; n1 is the number of turns of the wire rope on the balance friction drum; μ1 is the coefficient of friction between the wire rope and the balance friction drum.

[0036] Furthermore, an emergency braking verification system for a fully balanced wire rope winch-type ship lift includes:

[0037] The system equivalent mass calculation module is used to calculate the total equivalent mass M of the system under normal lifting conditions of the ship compartment, based on the operating characteristics of the fully balanced wire rope winch-type vertical ship lift. t1 The total equivalent mass M of the system under water leakage conditions t2 ;

[0038] The unbalanced load calculation module is used to calculate the unbalanced load on both sides of the drum under normal lifting conditions of the ship compartment, based on the operating characteristics of the fully balanced wire rope winch-type vertical ship lift. Unbalanced load F on both sides of the drum under water leakage conditions u2 ;

[0039] The translational acceleration calculation module is used to calculate the total equivalent mass M of the system under normal lifting and lowering conditions of the ship's cabin. t1 Unbalanced loads on both sides of the drum and the total equivalent mass M of the system under the condition of water leakage. t2 Unbalanced load F on both sides of the drum u2 In addition, the performance and parameters of the ship lift's safety braking system were determined, and the translational acceleration of the system during normal lifting and lowering of the ship compartment was calculated. The translational acceleration α of the system under the condition of water leakage w2 ;

[0040] The impact load coefficient calculation module is used to select the translational acceleration of the system during the normal lifting and lowering of the ship's compartment. The translational acceleration α of the system under the condition of water leakage w2 The maximum value in, combined with the dynamic load factor φ d Calculate the impact load factor K of the system. d ;

[0041] The wire rope strength verification module is used to verify the impact load coefficient K of the system. d Breaking tensile force T of steel wire rope s The number of wire ropes n2 and the safety factor k of the wire rope s Verify whether the strength of the steel wire rope under impact load meets the requirements;

[0042] The wire rope anti-slip verification module is used to verify the impact load coefficient K of the system. d counterweight M p Design water depth and water body weight (M) w Gravity balance weight M z Check whether there is slippage between the wire rope and the balance friction drum.

[0043] The present invention has the following beneficial effects:

[0044] 1) This invention addresses the frictional force transmission mechanism of the balanced friction drum and the operating characteristics of the fully balanced wire rope hoist ship lift. It specifically designs verification logic for two core working conditions: normal lifting and lowering of the ship compartment and water leakage. In particular, for the problem of sudden load change under the water leakage condition, it introduces the cooperative braking parameters of the balanced friction drum safety brake, which significantly improves the comprehensiveness and reliability of the verification under extreme scenarios and fills the gap in the existing technology for verification under extreme conditions.

[0045] 2) This invention breaks through the limitations of traditional single-index verification and establishes a multi-dimensional verification system of "impact load coefficient - wire rope strength - wire rope anti-slip", realizing the full-chain verification from load transfer to structural bearing capacity, from dynamic response to static safety, and effectively avoiding the safety risks that may be missed by single-index verification.

[0046] 3) The verification method of this invention has clear steps and well-defined formulas. The required parameters are all conventional parameters that can be directly obtained during the design and operation of the ship lift (such as ship weight, drum radius, braking torque, etc.), without the need for additional testing equipment or complex testing procedures. Engineering technicians can directly carry out verification work according to the steps and formulas in the claims. It is convenient to operate, highly efficient, and applicable to various types of fully balanced wire rope winch-type vertical ship lifts using balanced friction drums, and has broad engineering application value. Attached Figure Description

[0047] Figure 1 This is a flowchart of the emergency braking verification method for a fully balanced wire rope winch-type ship lift according to an embodiment of the present invention. Detailed Implementation

[0048] To make the objectives, technical solutions, and advantages of the embodiments of the present invention clearer, the technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0049] Please see Figure 1 This invention provides a method for verifying the emergency braking of a fully balanced wire rope winch-type ship lift, comprising the following steps:

[0050] Step 1: Total equivalent mass M of the system under normal lifting and lowering conditions of the ship's cabin t1 According to formula (1), the total equivalent mass M of the system under the water leakage condition is calculated. t2 Calculate according to formula (2):

[0051] (1);

[0052] (2);

[0053] In the formula, M t1 M is the total equivalent mass of the system under normal lifting and lowering conditions of the ship's cabin; t2 The total equivalent mass of the system under the condition of water leakage in the ship compartment; h is the water depth inside the compartment; L is the length of the ship compartment; ∆h is the depth of water during misloading; M w For the design water depth and water body weight; M s M represents the weight of the ship's compartment. p Total weight for counterweight; J d1 J represents the total rotational inertia of the main hoisting system without considering the balancing friction drum; d2 To account for the total rotational inertia of the main hoisting system of the balancing friction drum; r d Where is the radius of the roll.

[0054] Step 2: Calculate the unbalanced load on both sides of the drum during normal lifting and lowering of the ship's compartment according to formula (3). ; Calculate the unbalanced load F on both sides of the drum under the water leakage condition of the ship chamber according to formula (4). u2 :

[0055] (3);

[0056] (4);

[0057] In the formula, F u1 This refers to the unbalanced load on both sides of the drum during normal lifting and lowering of the ship's compartment; F u2 The unbalanced load on both sides of the drum under the condition of water leakage in the ship chamber; F k The unbalanced load is caused by factors such as system inertia, frictional resistance, wire rope stiffness resistance, and wind pressure; g is the acceleration due to gravity; h is the water depth inside the compartment; L is the length of the compartment; ∆h is the depth of the misloaded water; M w For the design water depth and water body weight; M s M represents the weight of the ship's compartment. p To balance the total weight.

[0058] Step 3: The safety braking system of the fully balanced wire rope winch-type vertical ship lift is activated by the safety brake on the lifting drum brake disc to apply emergency braking during normal lifting and lowering of the ship compartment; when the ship compartment experiences water leakage, the safety brake on both the lifting drum brake disc and the balance friction drum brake disc will apply emergency braking.

[0059] Step 4: When the ship is in normal lifting and lowering and emergency braking is applied, calculate the translational acceleration of the system according to formula (5):

[0060] (5);

[0061] In the formula, α w1 The translational acceleration of the system when applying emergency braking for normal raising and lowering of the ship's cabin; F s1 To increase the clamping force of a single brake head in the drum safety brake; s1 To increase the number of brake heads in the drum safety brake; μ s η is the coefficient of friction between the brake head and the brake disc. s For the efficiency of the safety brake; r s F is the braking radius; u1 This refers to the unbalanced load on both sides of the drum during normal lifting and lowering of the ship's compartment; M t1 The total equivalent mass of the system under normal lifting and lowering conditions of the ship's compartment.

[0062] Step 5: When applying emergency braking under the condition of water leakage in the ship compartment, calculate the translational acceleration of the system according to formula (6):

[0063] (6);

[0064] In the formula, α w2 F is the translational acceleration of the system when emergency braking is applied under conditions of water leakage in the ship's compartment; s2 To balance the clamping force of a single brake head in the friction drum safety brake; n s1 To balance the number of brake heads in the friction drum safety brake; F u2 The unbalanced load on both sides of the drum under the condition of water leakage in the ship chamber; M t2 The total equivalent mass of the system under the condition of water leakage in the ship compartment.

[0065] Step 6: Select the translational acceleration of the system during normal lifting and lowering of the ship's compartment. The translational acceleration α of the system under the condition of water leakage w2 The maximum value in, combined with the dynamic load factor φ d The impact load coefficient K of the system is calculated according to equation (7). d :

[0066] (7);

[0067] In the formula, K d α is the impact load factor of the system. max φ is the translational acceleration of the maximum system. d The dynamic load factor for emergency stop, unexpected stop, and non-continuous braking is set to 3.

[0068] Step 7: Under impact load conditions, the maximum tension of the wire rope should meet the requirements of equation (8):

[0069] (8);

[0070] In the formula, T s n is the breaking tensile strength of the wire rope; n2 is the number of wire ropes; k s The safety factor for the wire rope is taken as 7; h is the water depth inside the compartment; L is the length of the compartment; ∆h is the depth of water where the ship is overloaded; M w The design depth is the weight of the water body; g is the acceleration due to gravity; α w1 The translational acceleration of the system when applying emergency braking for normal raising and lowering of the ship's cabin; α w2 M is the translational acceleration of the system when emergency braking is applied under conditions of water leakage in the ship's compartment; s M represents the weight of the ship's compartment. p To balance the total weight.

[0071] Step 8: Based on the system's impact load coefficient K d counterweight M p Design water depth and water body weight (M) w Gravity balance weight M z Under impact load conditions, when equation (9) holds, the wire rope does not slip with the balance friction drum.

[0072] (9);

[0073] In the formula, M p To balance the weight; M w For the design water depth and water body weight; M z The equilibrium mass is the weight under gravity; g is the acceleration due to gravity; K d α is the impact load factor of the system. w2 n1 is the translational acceleration of the system when emergency braking is performed under the condition of water leakage in the ship chamber; n1 is the number of turns of the wire rope on the balance friction drum; μ1 is the coefficient of friction between the wire rope and the balance friction drum.

[0074] An emergency braking verification system for a fully balanced wire rope winch-type ship lift is described below:

[0075] The system equivalent mass calculation module is used to calculate the total equivalent mass M of the system under normal lifting conditions of the ship compartment, based on the operating characteristics of the fully balanced wire rope winch-type vertical ship lift. t1 The total equivalent mass M of the system under water leakage conditions t2 ;

[0076] The unbalanced load calculation module is used to calculate the unbalanced load on both sides of the drum under normal lifting conditions of the ship compartment, based on the operating characteristics of the fully balanced wire rope winch-type vertical ship lift. Unbalanced load F on both sides of the drum under water leakage conditions u2 ;

[0077] The translational acceleration calculation module is used to calculate the total equivalent mass M of the system under normal lifting and lowering conditions of the ship's cabin. t1 Unbalanced loads on both sides of the drum and the total equivalent mass M of the system under the condition of water leakage. t2 Unbalanced load F on both sides of the drum u2 In addition, the performance and parameters of the ship lift's safety braking system were determined, and the translational acceleration of the system during normal lifting and lowering of the ship compartment was calculated. The translational acceleration α of the system under the condition of water leakage w2 ;

[0078] The impact load coefficient calculation module is used to select the translational acceleration of the system during the normal lifting and lowering of the ship's compartment. The translational acceleration α of the system under the condition of water leakage w2 The maximum value in, combined with the dynamic load factor φ d Calculate the impact load factor K of the system. d ;

[0079] The wire rope strength verification module is used to verify the impact load coefficient K of the system. d Breaking tensile force T of steel wire rope s The number of wire ropes n2 and the safety factor k of the wire rope s Verify whether the strength of the steel wire rope under impact load meets the requirements;

[0080] The wire rope anti-slip verification module is used to verify the impact load coefficient K of the system. d counterweight M p Design water depth and water body weight (M) w Gravity balance weight M z Check whether there is slippage between the wire rope and the balance friction drum.

[0081] The technical solution of the present invention will be illustrated below with a specific example (a fully balanced wire rope winch-type vertical ship lift).

[0082] A fully balanced steel wire rope winch-type vertical ship lift has a lifting height of 88.8m, a ship compartment length of 144m, a width of 12.4m, a water depth of 3.9m, a ship compartment weight of 3500t, a design water depth and water body weight of 7200t, a counterweight weight of 10700t, and a steel wire rope diameter of 76mm suspending the ship compartment.

[0083] The main hoist consists of 8 sets of winch hoisting mechanisms, 8 sets of balanced friction drum assemblies, 1 set of mechanical synchronous shaft system, 4 sets of safety braking systems, 4 sets of dry oil lubrication systems, 1 set of maintenance platform, 1 set of main unit embedded parts, and corresponding electric drive, control, and testing equipment. Each set of winch hoisting mechanisms consists of 1 AC variable frequency motor, 1 reducer, 2 sets of hoisting drum assemblies, 2 sets of safety brakes, and 1 working brake. Each set of balanced drum assemblies consists of 1 drum assembly and 2 safety brakes.

[0084] Table 1 shows the relevant parameters for verifying the emergency braking system of a fully balanced wire rope winch-type vertical ship lift using a balanced friction drum.

[0085] Table 1 Main Calculation Parameters

[0086]

[0087] (1) Calculate the total equivalent mass of the system according to equations (1) to (2):

[0088] Total equivalent mass of the system under normal lifting conditions of the ship's cabin: M t1 =50654 t;

[0089] Total equivalent mass of the system under the condition of water leakage in the ship compartment: M t2 =43765 t;

[0090] (2) Calculate the unbalanced loads on both sides of the drum according to equations (3) to (4):

[0091] Unbalanced load on both sides of the drum during normal lifting and lowering of the ship's compartment: F u1 =10895kN;

[0092] Unbalanced load on both sides of the drum under the condition of water leakage in the ship chamber: F u2 =72740kN;

[0093] (3) According to formula (5), the following can be calculated:

[0094] The translational acceleration of the system when the ship's cabin is normally raised or lowered and then subjected to emergency braking is: α w1 =0.892m / s 2 ;

[0095] (4) According to formula (6), the following can be calculated:

[0096] The translational acceleration of the system when emergency braking is applied under conditions of water leakage in the ship's compartment: α w2 =0.902m / s 2 ;

[0097] (5) According to equation (7), the following can be calculated:

[0098] System impact load factor: K d =1.276;

[0099] (6) Determine whether the strength of the wire rope meets the requirements according to formula (8):

[0100] 127344kN;

[0101] ;

[0102] Equation (8) is valid, indicating that the strength of the wire rope meets the requirements.

[0103] (7) Determine whether there is slippage between the wire rope and the balance friction drum according to formula (9):

[0104] Left side of the inequality: ;

[0105] The right side of the inequality: ;

[0106] Equation (9) is valid, indicating that there will be no slippage between the wire rope and the friction drum.

[0107] This invention also provides an emergency braking verification system for a fully balanced wire rope winch-type ship lift, used to execute the emergency braking verification method for a fully balanced wire rope winch-type vertical ship lift as described above, including:

[0108] The system equivalent mass calculation module is used to calculate the total equivalent mass M of the system under normal lifting conditions of the ship compartment, based on the operating characteristics of the fully balanced wire rope winch-type vertical ship lift. t1 The total equivalent mass M of the system under water leakage conditions t2 ;

[0109] The unbalanced load calculation module is used to calculate the unbalanced load on both sides of the drum under normal lifting conditions of the ship compartment, based on the operating characteristics of the fully balanced wire rope winch-type vertical ship lift. Unbalanced load F on both sides of the drum under water leakage conditions u2 ;

[0110] The translational acceleration calculation module is used to calculate the total equivalent mass M of the system under normal lifting and lowering conditions of the ship's cabin. t1 Unbalanced loads on both sides of the drum and the total equivalent mass M of the system under the condition of water leakage. t2 Unbalanced load F on both sides of the drum u2 In addition, the performance and parameters of the ship lift's safety braking system were determined, and the translational acceleration of the system during normal lifting and lowering of the ship compartment was calculated. The translational acceleration α of the system under the condition of water leakage w2 ;

[0111] The impact load coefficient calculation module is used to select the translational acceleration of the system during the normal lifting and lowering of the ship's compartment. The translational acceleration α of the system under the condition of water leakage w2 The maximum value in, combined with the dynamic load factor φ d Calculate the impact load factor K of the system. d ;

[0112] The wire rope strength verification module is used to verify the impact load coefficient K of the system. d Breaking tensile force T of steel wire rope s The number of wire ropes n2 and the safety factor k of the wire rope s Verify whether the strength of the steel wire rope under impact load meets the requirements;

[0113] The wire rope anti-slip verification module is used to verify the impact load coefficient K of the system. d counterweight M p Design water depth and water body weight (M) w Gravity balance weight M z Check whether there is slippage between the wire rope and the balance friction drum.

[0114] This invention has the following features and effects:

[0115] 1. Enhancing the comprehensiveness and reliability of verification by addressing the characteristics and full operating conditions of the balanced friction drum: This invention specifically addresses the frictional force transmission mechanism of the balanced friction drum, establishing verification models for two core operating conditions: normal lifting and water leakage. In particular, for the problem of sudden load changes under the water leakage condition, the invention introduces the cooperative braking parameters of the balanced friction drum safety brake, which significantly enhances the verification coverage and reliability under extreme operating conditions, filling the gap in existing methods in this field.

[0116] 2. Establish a multi-dimensional linkage verification system of "impact load - wire rope strength - anti-slip performance": Breaking through the limitations of traditional single index verification, this invention organically combines the calculation of impact load coefficient with the verification of wire rope strength and anti-slip performance, realizing the full-chain safety verification from dynamic braking response to static structural bearing capacity, effectively identifying and avoiding the system risks that may be hidden due to isolated index verification.

[0117] 3. The method is highly practical and easy to apply and promote in engineering: The parameters involved in this invention are all conventional parameters in the design and operation of ship lifts. No additional testing equipment or complex tests are required. The verification steps are clear and the formulas are well-defined. Engineers can operate directly according to the steps. It is applicable to all types of fully balanced steel wire rope winch vertical ship lifts that use balanced friction drums. It has high operability and wide engineering applicability.

[0118] The above description is merely a specific embodiment of the present invention, but the scope of protection of the present invention is not limited thereto. Any variations or substitutions that can be easily conceived by those skilled in the art within the technical scope disclosed in the present invention should be included within the scope of protection of the present invention. Therefore, the scope of protection of the present invention should be determined by the scope of the claims.

Claims

1. A method for verifying the emergency braking of a fully balanced wire rope winch-type ship lift, characterized in that, Includes the following steps: Based on the operating characteristics of a fully balanced wire rope winch-type vertical ship lift, the total equivalent mass M of the system under normal lifting conditions of the ship compartment is calculated. t1 The total equivalent mass M of the system under water leakage conditions t2 And calculate the unbalanced load on both sides of the drum under normal lifting conditions of the ship's cabin. Unbalanced load F on both sides of the drum under water leakage conditions u2 ; Based on the total equivalent mass M of the system under normal lifting and lowering conditions of the ship's compartment t1 Unbalanced loads on both sides of the drum and the total equivalent mass M of the system under the condition of water leakage. t2 Unbalanced load F on both sides of the drum u2 In addition, the performance and parameters of the ship lift's safety braking system were determined, and the translational acceleration of the system during normal lifting and lowering of the ship compartment was calculated. The translational acceleration α of the system under the condition of water leakage w2 ; Select the translational acceleration of the system during normal lifting and lowering of the ship's cabin. The translational acceleration α of the system under the condition of water leakage w2 The maximum value in, combined with the dynamic load factor φ d Calculate the impact load factor K of the system. d ; Based on the system's impact load coefficient K d Breaking tensile force T of steel wire rope s The number of wire ropes n2 and the safety factor k of the wire rope s Verify whether the strength of the steel wire rope under impact load meets the requirements; Based on the system's impact load coefficient K d counterweight M p Design water depth and water body weight (M) w Gravity balance weight M z Check whether there is slippage between the wire rope and the balance friction drum; Based on the system's impact load coefficient K d Breaking tensile force T of steel wire rope s The number of wire ropes n2 and the safety factor k of the wire rope s To verify whether the strength of the wire rope under impact load meets the requirements, specifically including: under impact load conditions, the maximum tension of the wire rope meets the requirements of equation (8): （8）； In the formula, T s n is the breaking tensile strength of the wire rope; n2 is the number of wire ropes; k s The safety factor for the wire rope is taken as 7; h is the water depth inside the compartment; L is the length of the compartment; ∆h is the depth of water where the ship is overloaded; M w The design depth is the weight of the water body; g is the acceleration due to gravity; α w1 The translational acceleration of the system when applying emergency braking for normal raising and lowering of the ship's cabin; α w2 M is the translational acceleration of the system when emergency braking is applied under conditions of water leakage in the ship's compartment; s M represents the weight of the ship's compartment. p To balance the total weight; Based on the system's impact load coefficient K d counterweight M p Design water depth and water body weight (M) w Gravity balance weight M z To check whether there is slippage between the wire rope and the friction balance drum, specifically including: under impact load conditions, when equation (9) holds, there is no slippage between the wire rope and the friction balance drum: （9）； In the formula, M p To balance the weight; M w For the design water depth and water body weight; M z The equilibrium mass is the weight under gravity; g is the acceleration due to gravity; K d α is the impact load factor of the system. w2 n1 is the translational acceleration of the system when emergency braking is performed under the condition of water leakage in the ship chamber; n1 is the number of turns of the wire rope on the balance friction drum; μ1 is the coefficient of friction between the wire rope and the balance friction drum.

2. The method as described in claim 1, characterized in that, Based on the operating characteristics of a fully balanced wire rope winch-type vertical ship lift, the total equivalent mass M of the system under normal lifting conditions of the ship compartment is calculated. t1 The total equivalent mass M of the system under water leakage conditions t2 Specifically, this includes: the total equivalent mass M of the system under normal lifting and lowering conditions of the ship's cabin. t1 According to formula (1), the total equivalent mass M of the system under the water leakage condition is calculated. t2 Calculate according to formula (2): （1）； （2）； In the formula, M t1 M is the total equivalent mass of the system under normal lifting and lowering conditions of the ship's cabin; t2 The total equivalent mass of the system under the condition of water leakage in the ship compartment; h is the water depth inside the compartment; L is the length of the ship compartment; ∆h is the depth of water during misloading; M w For the design water depth and water body weight; M s M represents the weight of the ship's compartment. p Total weight for counterweight; J d1 J represents the total rotational inertia of the main hoisting system without considering the balancing friction drum; d2 To account for the total rotational inertia of the main hoisting system of the balancing friction drum; r d Where is the radius of the roll.

3. The method as described in claim 1, characterized in that, Based on the operating characteristics of a fully balanced wire rope winch-type vertical ship lift, the unbalanced loads on both sides of the drum under normal lifting conditions of the ship compartment are calculated. Unbalanced load F on both sides of the drum under water leakage conditions u2 Specifically, this includes: calculating the unbalanced load on both sides of the drum during normal lifting and lowering of the ship compartment according to formula (3). ; Calculate the unbalanced load F on both sides of the drum under the water leakage condition of the ship chamber according to formula (4). u2 : （3）； （4）； In the formula, F u1 This refers to the unbalanced load on both sides of the drum during normal lifting and lowering of the ship's compartment; F u2 The unbalanced load on both sides of the drum under the condition of water leakage in the ship chamber; F k The unbalanced loads are generated by system inertial force, frictional resistance, wire rope stiffness resistance, and wind pressure; g is the acceleration due to gravity; h is the water depth inside the compartment; L is the length of the compartment; ∆h is the depth of the misloaded water; M w For the design water depth and water body weight; M s M represents the weight of the ship's compartment. p To balance the total weight.

4. The method as described in claim 1, characterized in that, During normal lifting and lowering of the ship compartment, emergency braking is implemented by the safety brake installed on the lifting drum brake disc; when the ship compartment experiences water leakage, emergency braking is implemented by the safety brake installed on both the lifting drum brake disc and the balance friction drum brake disc.

5. The method as described in claim 4, characterized in that, When the ship's cabin is in normal lifting and lowering and emergency braking is applied, the translational acceleration of the system is calculated according to formula (5). : （5）； In the formula, α w1 The translational acceleration of the system when applying emergency braking for normal raising and lowering of the ship's cabin; F s1 To increase the clamping force of a single brake head in the drum safety brake; s1 To increase the number of brake heads in the drum safety brake; μ s η is the coefficient of friction between the brake head and the brake disc. s For the efficiency of the safety brake; r s r is the braking radius; d F is the radius of the drum; u1 This refers to the unbalanced load on both sides of the drum during normal lifting and lowering of the ship's compartment; M t1 The total equivalent mass of the system under normal lifting and lowering conditions of the ship's compartment.

6. The method as described in claim 5, characterized in that, When emergency braking is performed under the condition of water leakage in the ship compartment, the translational acceleration α of the system is calculated according to formula (6). w2 : （6）； In the formula, α w2 F is the translational acceleration of the system when emergency braking is applied under conditions of water leakage in the ship's compartment; s2 To balance the clamping force of a single brake head in the friction drum safety brake; n s2 To balance the number of brake heads in the friction drum safety brake; F u2 The unbalanced load on both sides of the drum under the condition of water leakage in the ship chamber; M t2 The total equivalent mass of the system under the condition of water leakage in the ship compartment.

7. The method as described in claim 1, characterized in that, Select the translational acceleration of the system during normal lifting and lowering of the ship's cabin. The translational acceleration α of the system under the condition of water leakage w2 The maximum value in, combined with the dynamic load factor φ d Calculate the impact load factor K of the system. d Specifically, this includes calculating the impact load coefficient K of the system according to equation (7). d : （7）； In the formula, K d φ is the impact load factor of the system. d The dynamic load factor for emergency stop non-continuous braking is set to 3.

8. An emergency braking verification system for a fully balanced wire rope winch-type ship lift, used to execute the method according to any one of claims 1-7, characterized in that, include: The system equivalent mass calculation module is used to calculate the total equivalent mass M of the system under normal lifting conditions of the ship compartment, based on the operating characteristics of the fully balanced wire rope winch-type vertical ship lift. t1 The total equivalent mass M of the system under water leakage conditions t2 ; The unbalanced load calculation module is used to calculate the unbalanced load on both sides of the drum under normal lifting conditions of the ship compartment, based on the operating characteristics of the fully balanced wire rope winch-type vertical ship lift. Unbalanced load F on both sides of the drum under water leakage conditions u2 ; The translational acceleration calculation module is used to calculate the total equivalent mass M of the system under normal lifting and lowering conditions of the ship's cabin. t1 Unbalanced loads on both sides of the drum and the total equivalent mass M of the system under the condition of water leakage. t2 Unbalanced load F on both sides of the drum u2 In addition, the performance and parameters of the ship lift's safety braking system were determined, and the translational acceleration of the system during normal lifting and lowering of the ship compartment was calculated. The translational acceleration α of the system under the condition of water leakage w2 ; The impact load coefficient calculation module is used to select the translational acceleration of the system during the normal lifting and lowering of the ship's compartment. The translational acceleration α of the system under the condition of water leakage w2 The maximum value in, combined with the dynamic load factor φ d Calculate the impact load factor K of the system. d ; The wire rope strength verification module is used to verify the impact load coefficient K of the system. d Breaking tensile force T of steel wire rope s The number of wire ropes n2 and the safety factor k of the wire rope s Verify whether the strength of the steel wire rope under impact load meets the requirements; The wire rope anti-slip verification module is used to verify the impact load coefficient K of the system. d counterweight M p Design water depth and water body weight (M) w Gravity balance weight M z Check whether there is slippage between the wire rope and the balance friction drum.

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