Electric winch and optimization method of power load and braking thereof

Abstract

The present invention relates to an electric winch and a method for optimizing its power load and braking. A comprehensive optimization solution is proposed for the safety hazards of traditional electric winches, such as power load overload and insufficient braking force. In terms of power load optimization, the invention method first measures the maximum load limit value of the winch, and sets two load safety thresholds accordingly. Then the current load is detected in real time, and the power output of the motor is dynamically adjusted according to the comparison result with the safety threshold. When the current load is between the two thresholds, the power is linearly adjusted according to a predetermined coefficient; when the maximum limit value is reached, the clutch is controlled to disengage the gear and immediately stop the winch operation. Multiple groups of coefficients can also be preset for different load weight ranges to make the power adjustment more accurate. In terms of brake optimization, an innovative auxiliary brake device is designed. The present invention comprehensively optimizes the power load control and braking performance of the electric winch, and significantly improves the performance of the equipment.

Description

Technical Field

[0001] The present invention relates to the technical field of winches, and in particular to a method and a device for optimizing a power load control and a braking system of an electric winch. Background Art

[0002] Electric winch is a common lifting equipment, widely used in various lifting, dragging and stretching operations. During the operation of electric winch, there is often a problem of unstable load, which can easily cause equipment overload and bring risks to equipment and operation safety. The main reasons for unstable load are:

[0003] 1. The load on the winch may change constantly due to work requirements, such as the weight of the hoisted object increases or decreases or the towed object encounters different resistances;

[0004] 2. The electric winch relies on a stable power supply. If the power supply voltage is unstable, it will affect the motor speed and torque output, causing load fluctuations;

[0005] 3. The internal mechanical parts of the winch, such as bearings and gears, may be worn or poorly lubricated, resulting in increased mechanical friction, affecting the normal operation of the winch and load stability;

[0006] 4. Control system failures, such as sensor damage, circuit problems, or software errors, may cause the system to be unable to accurately read load data or adjust motor output, causing load instability.

[0007] To solve this problem, it is necessary to optimize the power load control method and system of the electric winch.

[0008] On the other hand, in the current winch design, the brake device is also necessary and important. It needs to reliably lock the drum when the winch stops rotating, ensure the stability and safety of the traction load, and avoid potential risks caused by traction failure. Prior art such as Chinese patent CN203624946U discloses an improved brake device, which consists of an active seat, a reverse expansion torsion spring, a passive seat and a brake sleeve. When the brake is activated, the torsion spring expands to increase the friction and lock the winch. However, under extreme working conditions such as heavy load, high speed or high temperature environment, the braking force of a single torsion spring may not be sufficient, and there is a potential safety risk.

[0009] Therefore, it is necessary to design a more reliable and powerful braking mechanism or develop an auxiliary braking device to intervene in critical situations to avoid or reduce accidents and to ensure that the system can operate safely and efficiently under various working conditions to the maximum extent. The present invention proposes an innovative optimization solution for the above-mentioned problems of electric winch in terms of power load control and braking. Summary of the invention

[0010] In view of the above problems, the present invention provides a method for optimizing the power load and braking force of an electric winch, by setting multiple load safety thresholds and dynamically adjusting the motor power output according to the comparison results between the current load and these thresholds, and introducing an auxiliary braking device to supplement the braking force of the main braking device, thereby achieving precise control of the power load and braking force of the winch and improving the safety and reliability of the work.

[0011] The invention objective of the present invention is achieved through the following technical scheme: A method for optimizing the power load and brake of an electric winch, comprising the following steps:

[0012] a) Directly measure the maximum load limit value that the winch can bear based on the load sensor, and set two load safety thresholds according to the limit value;

[0013] b) Detect the current load in real time and compare the detected value with two safety thresholds;

[0014] c) dynamically adjusting the motor output power according to the comparison result, wherein when the current load is between two thresholds, the power is linearly adjusted according to a predetermined coefficient;

[0015] d) When the detected current load reaches the maximum limit, the winch is immediately stopped by controlling the clutch to disengage the gear;

[0016] e) An auxiliary braking device is provided, which includes an execution and driving assembly and a reset assembly. The execution and driving assembly includes a movable sleeve, a start trigger, a start actuator and an actuator. When the braking force of the main brake device is insufficient, the auxiliary braking device automatically intervenes to apply additional braking force to the winch drum;

[0017] f) The reset assembly of the auxiliary braking device includes a long strip hole slot opened on the periphery of the movable sleeve and an elastic member arranged in the hole slot, which is used to automatically reset the movable sleeve to its original position after braking.

[0018] Preferably, a plurality of groups of coefficients are pre-set for different winch load weight ranges, and a corresponding group of coefficients is dynamically selected according to the detected current load weight.

[0019] The present application also provides an electric winch power load optimization system, comprising:

[0020] a) Load monitoring module, used to monitor the load of the winch in real time;

[0021] b) a control module, used to adjust the motor output power according to the monitored load data;

[0022] c) The motor adjusts the output power according to the instructions of the control module.

[0023] Preferably, when the detected current load reaches the maximum limit value, the operation of the winch is stopped immediately by controlling the clutch to disengage the gear.

[0024] The present application also provides an electric winch auxiliary braking device, including an execution and driving component and a reset component, wherein the execution and driving component includes:

[0025] a) The movable sleeve is mounted on the outside of the brake sleeve of the main brake device of the winch;

[0026] b) A starter trigger, which is fixed in the movable sleeve and maintains dynamic contact with the reverse expansion torsion spring of the main brake device;

[0027] c) A starting actuator, fixed on the extended section of the movable sleeve;

[0028] d) The actuator, in cooperation with the starting actuator, can be movably installed up and down in the braking groove of the winch drum.

[0029] Preferably, a position control mechanism consisting of a push rod and a matching groove is provided between the starting actuator and the actuator.

[0030] Preferably, the matching groove is opened on one side of the actuator, the groove is upward, and the inner wall is gradually inclined from top to bottom.

[0031] Preferably, the reset assembly comprises an elongated slot formed on the periphery of the movable sleeve and an elastic member arranged in the slot.

[0032] Preferably, two annular movable grooves are provided on the brake sleeve of the winch main brake device, one of which is used to start the movement of the trigger member, and the other is used to start the movement of the actuator.

[0033] The present application also provides an electric winch, including a processor and a memory, wherein the memory stores program instructions, and when the program instructions are executed by the processor, the method for optimizing the power load and brake braking of the electric winch as described in any one of claims 1 to 2 is implemented.

[0034] Preferably, the program instructions include detecting the motor temperature of the winch, and controlling the opening state of the semiconductor refrigeration plate group according to the motor temperature and the heating rate.

[0035] In summary, the present invention has the following advantages compared with the prior art:

[0036] The embodiment of the present invention has the following advantages due to the adoption of the above technical solution:

[0037] 1. The load sensor detects the current load Lnow when the electric winch is in working state, and compares the current load Lnow with the safety threshold. When the load approaches or reaches the preset load threshold, the control system will adjust the output power of the motor to prevent the equipment from overloading. When the load is too large or the motor stops rotating, the control system controls the clutch to disengage the gear and immediately stops the operation of the winch to protect the equipment from damage.

[0038] 2. The present invention sets multiple groups of semiconductor refrigeration plate groups, which can promptly start the corresponding number of semiconductor refrigeration plate groups when the motor is overheated or the heating rate is too high. The multiple groups of semiconductor refrigeration plate groups working together can dissipate the internal heat of the electric winch in time, improve the stability of the electrical system, and improve the safety and thermal stability of the electric winch. It can also start the corresponding number of semiconductor refrigeration plate groups when the motor temperature rises or the heating rate is normal, thereby avoiding excessive waste of resources.

[0039] 3. The present invention introduces an auxiliary braking device. When the braking force of the main brake device is insufficient, the auxiliary braking device automatically intervenes to apply additional braking force to the winch drum, thereby improving the braking safety and reliability of the winch. The auxiliary braking device adopts an innovative position control mechanism of a push rod and a bevel matching groove, which can accurately control the active position of the actuator to ensure that it is reliably inserted into the braking groove of the winch drum to play an auxiliary braking role. The reset component of the auxiliary braking device realizes the automatic reset function through a simple long strip hole groove and elastic part design, avoiding manual reset and improving the efficiency and convenience of use. A movable groove is opened on the brake sleeve of the main brake device to provide necessary activity space for the movement of the components of the auxiliary braking device, ensuring efficient and smooth interaction between the components.

[0040] In general, the present invention comprehensively optimizes the power load control and braking capability of the electric winch, greatly improving the working safety, reliability and ease of use of the winch. BRIEF DESCRIPTION OF THE DRAWINGS

[0041] Figure 1 It is a schematic structural diagram of the winch of the present invention;

[0042] Figure 2 It is a logic flow chart of the electric winch power load optimization method;

[0043] Figure 3 It is a logic flow chart of the braking optimization method of electric winch brake;

[0044] Figure 4 A view showing some components of the execution and drive components and the reset components separated to better understand their construction and relationship to each other;

[0045] Figure 5A relative position diagram of the auxiliary brake device 1 after being installed in the main brake device 001 is provided, through which the specific layout of the auxiliary brake device in the brake system can be understood;

[0046] Figure 6 In order to clearly show the positional relationship between the various components inside the braking device, the reel is split into two parts and removed to expose the internal structure. In this figure, it can be seen that the rod-shaped member 117 has been separated from the groove with which it cooperates, and the actuator 115 is about to fall into the working position;

[0047] Figure 7 Shows the Figure 6 After comparing the state, the actuator 115 has moved down to the stop groove 116. At this time, although the opening of the matching groove and the position of the rod-shaped member 117 are still roughly corresponding, the entire mechanism has been activated to achieve the auxiliary braking effect.

[0048] The serial numbers in the figure are: main brake device 001, reel 002, brake sleeve 01, mounting hole 02, reverse expansion torsion spring 03, first movable groove 04, second movable groove 05, auxiliary braking device 1, execution and driving assembly 11, movable sleeve 112, starting trigger member 113, starting actuator 114, actuator 115, braking groove 116, rod-shaped member 117, matching groove 118, reset assembly 12, long strip hole groove 121, elastic member 122. DETAILED DESCRIPTION

[0049] Below are all the attached Figure 1-7 The embodiments of the present disclosure are described in detail.

[0050] Example 1

[0051] A method for optimizing power load of an electric winch comprises the following steps:

[0052] 1. Directly measure the maximum load limit value Lmax that the winch can bear based on the load sensor. According to the measured load limit value Lmax, set two load safety thresholds Lm and Ln, and their size relationship is Lm <Ln<Lmax。

[0053] 2. During the operation of the winch, the current load Lnow is detected in real time based on the load sensor, and the detected current load Lnow is compared with the two pre-set safety thresholds Lm and Ln. The following operations are performed according to the comparison results:

[0054] (1) If Lnow is less than Lm, the current output power of the motor is maintained unchanged.

[0055] (2) If Lnow is between Lm and Ln (Lm < Lnow < Ln), the output power P of the motor is adjusted according to the following formula: P = Lnow * Ka

[0056] where Ka is a coefficient, and the method for obtaining Ka includes:

[0057] First, when Lnow reaches Lm, record the value Pm of the current motor output power;

[0058] Then, when Lnow reaches Ln, record the value Pn of the current motor output power;

[0059] Under the condition of the same winch load weight, record the time difference Ta = Tm - Tn required for Lnow to rise from Lm to Ln (Tm is the moment when Lm is reached, and Tn is the moment when Ln is reached);

[0060] According to the above-recorded Pm, Pn, Lm, Ln, and Ta, calculate the value of Ka according to the formula Ka = (Pm - Pn) / (Lm - Ln) / Ta.

[0061] (3) For further optimization, the method further includes:

[0062] According to different winch load weights, preset multiple groups of Ka coefficient groups, each group corresponding to a load weight range;

[0063] When Lnow is between Lm and Ln, detect the current winch load weight and find the corresponding Ka coefficient group;

[0064] Assign the coefficient value of the Ka coefficient group to Ka for adjusting the calculation of the motor output power P.

[0065] By setting multiple groups of Ka coefficients, the method can more accurately control the motor power output for different load conditions, making the load control more precise.

[0066] 3. If Lnow exceeds Ln but is still less than Lmax, the output power P of the motor is adjusted according to the following formula: P = Lnow * Kb

[0067] where Kb is another coefficient, and the method for obtaining Kb includes:

[0068] First, when Lnow reaches Ln, record the current motor output power Pn;

[0069] Record the time difference Tb = Tnax - Tn required for Lnow to rise from Ln to Lmax (Tnax is the moment when Lmax is reached);

[0070] According to Pn, Lmax, Ln and Tb, the value of Kb is calculated according to the formula Kb = (Pmax-Pn) / (Lmax-Ln) / Tb. Pmax is the maximum allowable output power of the motor.

[0071] Also for optimization, this part can preset multiple sets of Kb coefficients for adjustment according to different load weight ranges.

[0072] 4. When Lnow reaches Lmax, the control system controls the clutch to disengage the gear and immediately stops the winch to protect the equipment from damage.

[0073] Through the above method, the electric winch can dynamically adjust the motor power output according to the real-time load conditions to keep the load within a safe range, thereby optimizing load control and improving work safety and reliability.

[0074] In practical applications, for different winch load weight ranges, it is necessary to pre-test and determine the corresponding Ka and Kb coefficient groups:

[0075] 1. For Ka coefficient group:

[0076] When the test winch load weight is in the range of 5-10kg, determine a set of Ka coefficients, recorded as K1;

[0077] When testing the load weight range of 10-20kg, determine another set of Ka coefficients, recorded as K2;

[0078] When testing the load weight range of 20-50kg, another set of Ka coefficients is determined, recorded as K3;

[0079] By analogy, corresponding Ka coefficient groups can be set in advance for different load weight ranges.

[0080] 2. During actual use, it is necessary to detect the current winch load weight in real time.

[0081] Assuming that the current winch load weight is detected to be 25kg, it belongs to the load weight range of 20-50kg;

[0082] At this time, the coefficient value of the predetermined K3 coefficient group is assigned to Ka for calculation when adjusting the motor power output.

[0083] 3. When Lnow exceeds Ln but is still less than Lmax, the motor output power P needs to be adjusted. The formula is:

[0084] P=Lnow*Kb

[0085] Where Kb is another coefficient, the steps to obtain Kb are:

[0086] (1) When Lnow reaches Ln, record the current motor output power value Pn;

[0087] (2) Record the time difference Tb = Tnax - Tn required for Lnow to rise from Ln to Lmax

[0088] Where Tnax is the moment when Lnow reaches Lmax, and Tn is the moment when Lnow reaches Ln;

[0089] (3) Based on the recorded Pn, Lmax, Ln and Tb, use the formula:

[0090] Kb = (Pmax - Pn) / (Lmax - Ln) / Tb

[0091] The value of Kb is calculated.

[0092] Where Pmax is the maximum allowable output power of the motor.

[0093] 4. Also for optimization, when determining Kb, multiple groups of Kb coefficient groups can be pre-set according to different winch load weight ranges.

[0094] (1) For example, determine a set of Kb factors when testing a load range of 5-10kg;

[0095] (2) Identify another group when testing the 10-20kg range;

[0096] (3) another group was identified when testing the 20-50kg range;

[0097] 5. In actual use, it is necessary to detect the current load weight of the winch in real time.

[0098] Assuming that the current winch load is detected to be 25kg, it belongs to the load range of 20-50kg;

[0099] At this time, the set of Kb coefficient values ​​pre-determined for the 20-50kg load range is assigned to Kb for calculation when adjusting the motor power output.

[0100] Through the above method, more accurate Ka and Kb coefficients can be used for different load weight conditions, thereby optimizing the adjustment of motor power output and making load control more accurate and reasonable.

[0101] More specifically, when Lnow is less than Lmax but greater than Ln, the formula for adjusting the motor output power P is:

[0102] P=Lnow*KbWhen using this formula to adjust the motor power output, it is also necessary to combine the actual load weight of the current winch. The specific steps are as follows:

[0103] 1. Before applying this method, it is necessary to pre-test and determine multiple Kb coefficient groups for different winch load weight ranges. Each Kb coefficient group corresponds to a specific winch load weight range.

[0104] 2. Taking practical application as an example, the Kb coefficient group can be determined as follows:

[0105] When the load weight of the test winch is in the range of 5-10kg, a set of Kb coefficients is determined and recorded as Kb1;

[0106] When testing the load weight range of 10-20kg, determine another set of Kb coefficients, recorded as Kb2;

[0107] When testing the load weight range of 20-50kg, another set of Kb coefficients is determined, recorded as Kb3;

[0108] Similarly, corresponding Kb coefficient groups can be set in advance for more load weight ranges.

[0109] 3. In actual use, it is necessary to detect the current load weight value of the winch in real time.

[0110] 4. According to the detected current load weight value, determine which pre-set load weight range it belongs to.

[0111] 5. Assign the coefficient value of the Kb coefficient group predetermined for the load weight range to Kb in the formula.

[0112] 6. Taking the above 5-10kg, 10-20kg, 20-50kg as an example:

[0113] Assuming that the current winch load weight is detected to be 25kg, it belongs to the load weight range of 20-50kg;

[0114] At this time, the set of Kb coefficients pre-determined for the load range of 20-50kg, i.e., the value of Kb3, is assigned to Kb;

[0115] Then, according to the formula P=Lnow*Kb, substitute the value of Kb3 into Kb to calculate the adjusted motor power output P.

[0116] In this way, within the range of Lnow less than Lmax but greater than Ln, the corresponding optimal Kb coefficient group can be dynamically selected according to the current actual load weight, making the adjustment of the motor power output more accurate and reasonable, and further optimizing the load control effect.

[0117] In actual application, for example, when the test winch load weight is 5-10Kg group, the coefficient group K1 is determined, when the test winch load weight is 10-20Kg group, the coefficient group K2 is determined, when the test winch load weight is 20-50Kg group, the coefficient group K3 is determined, and when the current winch load weight is detected to be 25Kg, the coefficient group K3 is replaced by Kb.

[0118] When Lnow reaches Lmax, the control system immediately stops the operation of the winch by controlling the clutch to disengage the gear to protect the equipment from damage.

[0119] On the basis of the above scheme, as a further preferred embodiment of the present technical scheme, it also includes detecting the current motor temperature, and installing a plurality of semiconductor refrigeration sheet groups on the housing of the electric winch, and the opening strategy of the semiconductor refrigeration sheet group is as follows:

[0120] And detect the current motor temperature Tenow, detect it every ten seconds, and determine the current motor heating rate HRnow;

[0121] Determine the number of semiconductor cooling plate groups to be opened according to the motor heating rate HR and the motor temperature Tenow;

[0122] Prior to this, the heat dissipation efficiency of the semiconductor refrigeration sheet group is obtained;

[0123] Set the semiconductor refrigeration plate group start threshold (B1, B2, B3), where each threshold B1, B2, B3 corresponds to a separate motor temperature Te and heating rate HR, that is, B1 corresponds to Te1 and HR1, B2 corresponds to Te2 and HR2, B3 corresponds to Te3 and HR3, Te1<Te2<Te3, HR1<HR2<HR3, when any one of the motor temperature Tenow, the motor heating rate HR and the motor temperature Tenow reaches the set conditions of the thresholds B1, B2, B3, turn on the preset semiconductor refrigeration plate group.

[0124] More specifically, B1 can set the number of open groups to 20% of the total number of semiconductor refrigeration groups, B2 can set the number of open groups to 50% of the total number of semiconductor refrigeration groups, and B3 can set the number of open groups to 100% of the total number of semiconductor refrigeration groups, which is specifically determined based on the heat dissipation efficiency of the semiconductor refrigeration groups.

[0125] In order to solve the above technical problems, another technical solution adopted in this application is: an electric winch power load optimization system, which includes:

[0126] Load monitoring module, used to monitor the load condition of the winch in real time;

[0127] A control module receives data from the load monitoring module and adjusts the output power of the motor and controls the action of the clutch according to the data;

[0128] As well as the motor and clutch, they act according to the instructions of the control module.

[0129] To solve the above technical problems, another technical solution adopted in the present application is: a computer device, which includes a processor and a memory coupled to the processor, wherein program instructions are stored in the memory, and when the program instructions are executed by the processor, the processor executes the steps of the electric winch power load optimization method and system as described above.

[0130] In order to solve the above technical problems, another technical solution adopted in the present application is: a storage medium storing program instructions capable of implementing the electric winch power load optimization method and system as described above.

[0131] Example 2

[0132] On the basis of the original embodiment, the present invention has innovatively optimized the brake system of the winch, and added an auxiliary braking device 1, which gives the winch higher braking safety performance.

[0133] The auxiliary braking device 1 is designed to be installed between the main brake device 001 and the winch drum 002. Its function is to automatically intervene and apply additional braking force to the drum 002 when the braking force of the main brake device 001 is insufficient to completely stop the rotation of the drum 002, thereby ensuring that the winch is reliably stopped and avoiding potential safety accidents.

[0134] In order to reserve installation space for the auxiliary braking device 1, the free end of the brake sleeve 01 of the main brake device 001 is specially extended to form an extension section. The extension section extends a small section outward along the axial direction of the brake sleeve 01, and a mounting hole 02 is opened on this small section for fixing the actuator of the auxiliary braking device 1.

[0135] The auxiliary braking device 1 is composed of two subsystems, namely, an execution and driving component 11 and a reset component 12, which are arranged in the outer circumference area of ​​the brake sleeve 01, including the extension section.

[0136] The execution and driving component 11 is the key to realize the auxiliary braking function, and it includes the following main components:

[0137] The movable sleeve 112 is an annular structure, which is sleeved on the outer ring of the brake sleeve 01 and extends a protruding section 111 toward one side of the free end, serving as the main body foundation of the entire driving component;

[0138] The start trigger 113 is fixedly mounted on the inner wall of the movable sleeve 112 and maintains dynamic contact with the reverse expansion torsion spring 03 of the main brake device 001 to obtain the movement information of the reverse expansion torsion spring 03;

[0139] Start the actuator 114 - fixedly mounted on the extended section 111 of the movable sleeve 112;

[0140] Actuator 115 - cooperates with the start actuator 114 and can be movably installed in the mounting hole 02 up and down;

[0141] Stop groove 116 - At the position corresponding to the actuator 115 on the inner wall of the reel 002, a plurality of such stop grooves 116 are arranged along the circumference array.

[0142] During operation, if the braking force of the main brake device 001 is insufficient and the reel 002 cannot be completely stopped from rotating, the reverse expansion torsion spring 03 will push the start trigger 113 to move, thereby driving the movable sleeve 112 to move toward the free end. The start actuator 114 on the movable sleeve 112 then drives the actuator 115 to move downward, and the actuator 115 will be stuck in the stop groove 116, producing a blocking and braking effect on the reel 002, thereby completely stopping the reel 002 from continuing to rotate.

[0143] In the design of the auxiliary braking device 1, an innovative position control mechanism is used between the starting actuator 114 and the actuator 115. Through the combination of the push rod and the matching groove, the active position of the actuator 115 can be accurately controlled.

[0144] Specifically, one end of the start actuator 114 is connected to a rod-shaped member 117 extending along the axial direction of the brake sleeve 01. The cross section of the rod-shaped member 117 is circular so as to facilitate sliding assembly with the matching part. The actuator 115 has a matching groove 118 on one side that is gradually inclined from top to bottom. The opening end of the matching groove 118 is located at the highest point and gradually decreases toward the inner wall.

[0145] When the auxiliary braking device 1 is activated, the rod-shaped member 117 is inserted and moves downward along the matching groove 118. Due to the inclined structure of the matching groove 118, as the insertion depth of the rod-shaped member 117 increases, it will gradually push the actuator 115 to move linearly upward.

[0146] It should be noted that when installing the rod-shaped member 117, its insertion direction must strictly follow the specified direction, that is, when the brake fails, the reverse torsion spring 03 drives the trigger member 113 to move, and the rod-shaped member 117 must be moved in the direction of being gradually withdrawn from the matching groove 118.

[0147] The innovative push rod-bevel matching structure design cleverly converts the linear motion of the start actuator 114 into a compound motion form of the rise and fall of the actuator 115. Through this mechanism, the active position of the actuator 115 can be accurately controlled so that it can be reliably inserted into the stop groove 116 and effectively play the auxiliary braking role.

[0148] In summary, this innovative design of the push rod and the matching groove not only solves the position control problem, but also has smooth movement and compact structure, fully reflecting the inventor's creativity and engineering technology level.

[0149] The reset component 12 of the auxiliary braking device 1 is a key part to realize the automatic reset function, and it includes the following two main components:

[0150] Long strip-shaped slots 121 - are provided on the periphery of the movable sleeve 112 and are distributed in the shape of long ring strips;

[0151] The elastic member 122 is a component with elastic restoring force such as a spring, and is arranged in the inner space of the long strip hole groove 121.

[0152] During installation, one end of the elastic member 122 is fixed to the brake sleeve 01 , and the other end is against the inner wall of the movable sleeve 112 .

[0153] When the auxiliary braking device 1 is in the standby state, the elastic member 122 has an elastic restoring force that continuously acts on the movable sleeve 112 due to the tensile deformation of the installation. This restoring force will make the movable sleeve 112 obtain a continuous rotation torque, and the direction of the torque is exactly opposite to the direction in which the start trigger member 113 is pushed by the reverse expansion torsion spring 03.

[0154] In other words, when in standby mode, the elastic member 122 applies a torque force to the movable sleeve 112 to rotate in the opposite direction, so that the movable sleeve 112 maintains a "reverse movement" trend and is in a standby ready state.

[0155] Once braking is required, the reverse expansion torsion spring 03 pushes the start trigger 113 to overcome the torque of the elastic member 122, and the movable sleeve 112 can smoothly rotate toward the free end, thereby driving the execution and driving component 11 to start working.

[0156] After the braking process is completed, when the reel rotates in the opposite direction to make the actuator 115 automatically disengage from the braking groove 116, the elastic potential energy stored in the elastic member 122 will be re-emerged to generate a restoring torque in the opposite direction, pulling the movable sleeve 112 back to the original position for standby state.

[0157] Therefore, the reset component 12 relies on the design of simple long strip holes and elastic parts to provide power for the movable sleeve 112 to work normally, and can automatically reset after braking, so that the entire system can operate efficiently, avoiding the need for manual reset, and greatly improving the efficiency and convenience of use.

[0158] In the design of the auxiliary braking device 1, the start trigger 113 and the start actuator 114 in the execution and driving assembly 11 need to be arranged in the internal space of the brake sleeve 01. In order to avoid interference between them and the inner wall of the brake sleeve 01 and ensure that they can move freely, a special activity channel needs to be opened on the brake sleeve 01.

[0159] Specifically, along the radial direction of the brake sleeve 01, two annular movable grooves are provided:

[0160] The first movable groove 04 - its function is to reserve enough space for the movement of the start trigger 113, so that it can move freely with the action of the reverse expansion torsion spring 03;

[0161] The second movable groove 05 - its function is to free up necessary movable space for the action of the starting actuator 114 to avoid being hindered by the inner wall of the brake sleeve 01 and affecting its normal operation.

[0162] The setting of these two movable grooves allows the start trigger member 113 and the start actuator 114 to have sufficient room for movement in the radial direction, and their movement will no longer be restricted or interfered by the inner wall of the brake sleeve 01, ensuring efficient and smooth interaction with other components such as the reverse expansion torsion spring 03.

[0163] This design effectively avoids the risk of collision and interference between components during movement, ensuring that the entire execution and driving mechanism can operate efficiently, reliably and in a coordinated manner, thereby providing an important structural foundation for the normal operation of the auxiliary braking device 1.

Claims

1. A method for optimizing power load and brake of electric winch, characterized in that: The following steps are involved: a) Directly measure the maximum load limit value that the winch can bear based on the load sensor, and set two load safety thresholds according to the limit value; b) Detect the current load in real time and compare the detected value with two safety thresholds; c) dynamically adjusting the motor output power according to the comparison result, wherein when the current load is between two thresholds, the power is linearly adjusted according to a predetermined coefficient; d) When the detected current load reaches the maximum limit, the winch is stopped immediately by controlling the clutch to disengage the gear; e) An auxiliary braking device is provided, which includes an execution and driving assembly and a reset assembly. The execution and driving assembly includes a movable sleeve, a start trigger, a start actuator and an actuator. When the braking force of the main brake device is insufficient, the auxiliary braking device automatically intervenes to apply additional braking force to the winch drum; f) The reset assembly of the auxiliary braking device includes a long strip hole slot opened on the periphery of the movable sleeve and an elastic member arranged in the hole slot, which is used to automatically reset the movable sleeve to its original position after braking.

2. The method according to claim 1, characterized in that For different winch load weight ranges, multiple groups of coefficients are pre-set, and the corresponding coefficient group is dynamically selected according to the detected current load weight.

3. An electric winch auxiliary braking device, characterized in that: It includes an execution and driving component and a reset component, and the execution and driving component includes: a) The movable sleeve is mounted on the outside of the brake sleeve of the main brake device of the winch; b) A starter trigger, which is fixed in the movable sleeve and maintains dynamic contact with the reverse expansion torsion spring of the main brake device; c) A starting actuator, fixed on the extended section of the movable sleeve; d) The actuator, in cooperation with the starting actuator, can be movably installed up and down in the braking groove of the winch drum.

4. The auxiliary braking device according to claim 3, characterized in that: A position control mechanism consisting of a push rod and a matching groove is arranged between the starting actuator and the actuator.

5. The auxiliary braking device according to any one of claims 3 to 4, characterized in that: The resetting component comprises a long strip hole groove opened on the periphery of the movable sleeve and an elastic member arranged in the hole groove.

6. The auxiliary braking device according to claim 5, characterized in that: Two annular movable grooves are provided on the brake sleeve of the main brake device of the winch, one of which is used to start the movement of the trigger member, and the other is used to start the movement of the actuator.

7. An electric winch, characterized in that: The invention comprises a processor and a memory, wherein the memory stores program instructions, and when the program instructions are executed by the processor, the method for optimizing the power load and brake of the electric winch as claimed in any one of claims 1 to 2 is implemented.

8. The electric winch according to claim 7, wherein the program instructions include detecting the motor temperature of the winch and controlling the opening state of the semiconductor refrigeration plate group according to the motor temperature and the heating rate.

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