Double-transmission-ratio switching gearbox and double-transmission gear shifting path thereof

Abstract

The invention belongs to the technical field of gear box structures, and particularly relates to a double-transmission-ratio switching gear box and a double-transmission gear shifting path thereof.The double-transmission-ratio switching gear box comprises a lower box body and an upper box body, and a first-stage shaft, a second-stage shaft, an intermediate shaft and a third-stage shaft are jointly installed in an inner cavity of the lower box body and an inner cavity of the upper box body; through the innovative structure that the three-stage parallel shafts and the double electromagnetic clutches are matched, precise switching between the cable winding working condition and the cable unwinding working condition is achieved. When the cable is collected, the transmission system operates at a high rotating speed and a low torque, and the requirement for rapid lifting is met; and during cable laying, the cable is output at a lower rotating speed and a higher torque, so that stable laying is ensured.

Description

Technical Field

[0001] This invention belongs to the field of gearbox structure technology, specifically relating to a dual transmission ratio switching gearbox and its dual transmission shifting path. Background Technology

[0002] Against the backdrop of a shift towards a cleaner and lower-carbon energy structure, high-altitude wind power technology, with its advantage of capturing more stable and powerful wind energy at higher altitudes, has become an important development direction in the new energy field. High-altitude wind power systems typically use high-strength cables to elevate the power generation equipment to altitudes of hundreds or even thousands of meters. The cable retrieval (lifting) and cable deployment (lowering) operations are crucial aspects of system deployment, operation, maintenance, and safe recovery. As the core power transmission component of the cable retrieval / deployment system, the gearbox's performance directly affects the efficiency, reliability, and lifespan of the entire system.

[0003] Currently, cable take-up / deployment drive systems used in such scenarios mainly face the following technical challenges:

[0004] 1. A single transmission ratio cannot meet the demands of dual operating conditions: Cable winding requires a high linear speed and low torque to rapidly lift the power generation unit; while cable unwinding requires a lower linear speed and higher torque to ensure smooth and controlled unwinding. Traditional gearboxes often use a fixed single transmission ratio design, making it difficult to optimize two drastically different operating conditions simultaneously. If the transmission ratio favors cable winding efficiency, excessively high speeds during cable unwinding can lead to impacts, vibrations, or even loss of control; if it favors unwinding stability, cable winding efficiency is low, resulting in significant energy loss (up to 10% or more), making it difficult to balance the contradiction between "high efficiency" and "smoothness."

[0005] 2. Transient shock and vibration issues during gear shifting: If a switchable gear ratio scheme is used, the stiffness of the transmission chain will change abruptly when switching between cable reeling and unloading modes. Combined with the instantaneous engagement / disengagement of the clutch, this can easily trigger strong coupled vibrations and impact loads. The document indicates that such transient impact loads can reach 1.3 times the steady-state load. This impact will not only significantly increase the contact stress of critical components such as gears and bearings, accelerating tooth surface wear and pitting, but will also cause structural fatigue damage, seriously threatening the long-term operational reliability of aerial work platforms (which have extremely high maintenance costs). Summary of the Invention

[0006] To address the problems mentioned in the background section, this invention provides a dual-transmission ratio switching gearbox and its dual-transmission shifting path, which offers the advantages of precise dual-transmission ratio switching while balancing cable retrieval efficiency and cable release stability.

[0007] To achieve the above objectives, the present invention provides the following technical solution: a dual transmission ratio switching gearbox, comprising a lower housing and an upper housing, wherein a primary shaft, a secondary shaft, an intermediate shaft, and a tertiary shaft are jointly installed in the inner cavities of the lower housing and the upper housing; a gear one is fixedly mounted through the primary shaft, a gear two and a gear three are fixedly mounted through the secondary shaft, the gear three being located below the gear two, and the gear two meshing with the gear one; a gear four, a cable release driven gear, and a cable take-up driven gear are fixedly mounted through the intermediate shaft, the gear four meshing with the gear three; a tertiary take-up gear and a tertiary cable release gear are fixedly mounted through the tertiary shaft, the tertiary take-up gear meshing with the take-up driven gear, and the tertiary cable release gear meshing with the cable release driven gear; the intermediate shaft is also provided with a cable release end electromagnetic clutch and a cable release end electromagnetic clutch.

[0008] As a preferred embodiment of the dual transmission ratio switching gearbox of the present invention, the total length of the primary shaft, secondary shaft, intermediate shaft and tertiary shaft is 810mm, and all of them are made of 45 steel with heat treatment.

[0009] As a preferred embodiment of the dual transmission ratio switching gearbox of the present invention, the first gear has 18 teeth, the second gear has 90 teeth and a module of 16mm; the third gear has 20 teeth, the fourth gear has 120 teeth and a module of 16mm; the winding driven gear has 36 teeth, the third-stage winding gear has 100 teeth and a module of 16mm; the unwinding driven gear has 20 teeth, the third-stage unwinding gear has 116 teeth and a module of 16mm.

[0010] As a preferred embodiment of the dual transmission ratio switching gearbox of the present invention, both the take-up electromagnetic clutch and the release electromagnetic clutch are magnetically attracted electromagnetic clutches with a rated torque ≥25kN・m. They are connected to the intermediate shaft using a spline connection, with the clutch driving end measuring 85×42mm, the driven end measuring 80×28mm, and the engagement gap measuring 2mm.

[0011] As a preferred embodiment of the dual transmission ratio switching gearbox of the present invention, an isolation shoulder with a diameter of 190mm is provided on the intermediate shaft between the electromagnetic clutch at the cable take-up end and the electromagnetic clutch at the cable release end, which is used to mechanically prevent the dual clutches from colliding and interfering during gear shifting.

[0012] As a preferred embodiment of the dual transmission ratio switching gearbox of the present invention, the two ends of the three-stage shaft are respectively provided with self-aligning roller bearings and deep groove ball bearings, the two ends of the intermediate shaft are provided with deep groove ball bearings, and the cable take-up driven gear and the cable release driven gear are respectively supported on the intermediate shaft by double deep groove ball bearings.

[0013] A dual-transmission ratio switching gearbox with a dual-transmission shifting path, applicable to the aforementioned dual-transmission ratio switching gearbox, includes the following steps:

[0014] Step 1: The control unit is powered on and collects the system status, including clutch position, motor speed, and load sensor signals. It determines whether the current requirement is cable winding or cable unwinding. If it needs to start from a standby state, the motor is controlled to enter standby mode, at which time the motor idles at low speed or maintains zero torque. If it needs to switch between cable winding and unwinding, the subsequent gear shifting process is executed.

[0015] Step 2: If it is a gear shifting operation, first control the electromagnetic clutch coil on the currently engaged side to de-energize, the electromagnetic force disappears, and under the action of the release spring, the clutch driving end and driven end separate, with a response time ≤0.23s. At the same time, control the motor to adjust the speed: if switching from cable take-up to cable release, actively reduce the motor speed from the rated speed to the target speed, so that the speed of the cable release driven gear on the intermediate shaft that is about to engage is close to the output speed of the motor after the first two stages of reduction, so as to reduce the meshing impact;

[0016] Step 3: In terms of electrical control, the interlock relay ensures that the original clutch is completely de-energized and the status feedback is "disengaged". The control system sends a pre-position signal to the target clutch, and the coil is ready to be energized.

[0017] Step 4: The target clutch coil is energized, generating an electromagnetic attraction force of ≥1820N, which overcomes the release spring force and quickly closes within the set engagement gap of 2mm, with a response time ≤0.32s. The clutch driving end is rigidly connected to the intermediate shaft, and the driven end is locked to the corresponding cable take-up driven gear or cable release driven gear via a flat key, thus establishing a complete power transmission path.

[0018] S1: Cable winding path: Motor → Primary shaft, Gear 1 → Secondary shaft, Gear 2, Gear 3 → Intermediate shaft, Gear 4 → Cable winding end electromagnetic clutch → Cable winding driven gear → Third stage cable winding gear → Drum;

[0019] S2: Cable release path: Motor → Primary shaft, Gear 1 → Secondary shaft, Gear 2, Gear 3 → Intermediate shaft, Gear 4 → Cable release end electromagnetic clutch → Cable release driven gear → Third stage cable release gear → Drum;

[0020] Step 5: After the clutch is fully engaged, the control system sends torque and speed commands to the motor according to the target operating conditions to smoothly apply the load. At the same time, the monitoring system collects data from vibration sensors and temperature sensors in real time, as well as feedback on motor current and clutch status, to ensure that there is no abnormal vibration, excessive temperature rise or electrical fault during gear shifting.

[0021] Step 6: The system enters steady-state operation, maintains the target transmission ratio, and the electrical interlock relay keeps the power supply circuit of the non-working side clutch disconnected to prevent both clutches from engaging simultaneously.

[0022] Step 7: When the system has been running stably under the target operating conditions for a set time or has met specific operating parameters, the control unit determines that the shift operation is complete and sends a "successful shift" signal and the current working mode signal, such as cable winding or cable unwinding, to the superior system or operating interface.

[0023] Compared with the prior art, the beneficial effects of the present invention are:

[0024] 1. Through an innovative structure of "three-stage parallel shaft + dual electromagnetic clutches", precise switching between cable winding and cable unwinding is achieved. When winding the cable, the transmission system operates at a higher speed and lower torque to meet the needs of rapid lifting; when unwinding the cable, it outputs at a lower speed and higher torque to ensure smooth lowering.

[0025] 2. The magnetic electromagnetic clutch features an electrical interlock design, ensuring fast shifting response and eliminating the risk of interference. By optimizing the clutch engagement clearance, gear profile, and synchronous adjustment of motor speed, sudden stiffness changes and coupled vibrations during gear shifting are effectively suppressed.

[0026] 3. The gearbox adopts a four-axis equal-length and modular layout, with optimized housing dimensions of 4500mm×2312mm×870mm, balancing internal space utilization and high-altitude installation limitations. The housing is equipped with axial heat sinks and a forced lubrication system to meet the heat dissipation requirements at 1MW power; the sealed structure is adaptable to high and low temperatures of -40℃ to 60℃ and humid environments. In addition, the housing has reserved maintenance holes and integrated sensors (vibration, temperature) to support condition monitoring and fault early warning, greatly improving the system's maintainability and environmental adaptability, and reducing the cost and risk of high-altitude operation and maintenance. Attached Figure Description

[0027] The accompanying drawings are provided to further illustrate the invention and form part of the specification. They are used in conjunction with embodiments of the invention to explain the invention and do not constitute a limitation thereof. In the drawings:

[0028] Figure 1 This is a schematic diagram of the external structure of the present invention;

[0029] Figure 2 This is a schematic diagram of the internal structure of the present invention;

[0030] Figure 3 This is a schematic diagram of the upper housing of the present invention;

[0031] Figure 4 This is a schematic diagram of the lower housing of the present invention.

[0032] In the diagram: 1. Lower housing; 2. Upper housing; 3. Primary shaft; 4. Secondary shaft; 5. Intermediate shaft; 6. Tertiary shaft; 7. Gear 1; 8. Gear 2; 9. Gear 3; 10. Gear 4; 11. Cable release driven gear; 12. Cable take-up driven gear; 13. Tertiary take-up gear; 14. Tertiary cable release gear; 15. Cable release end electromagnetic clutch; 16. Cable take-up end electromagnetic clutch. Detailed Implementation

[0033] 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, and 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.

[0034] like Figure 1-4 As shown: A dual-ratio switching gearbox includes a lower housing 1 and an upper housing 2. A primary shaft 3, a secondary shaft 4, an intermediate shaft 5, and a tertiary shaft 6 are installed together within the cavities of both housings. A gear 7 is fixedly mounted through the primary shaft 3. A gear 8 and a gear 9 are fixedly mounted through the secondary shaft 4, with the gear 9 located below the gear 8. The gear 8 meshes with the gear 7. A gear 10, a cable-laying driven gear 11, and a cable-reeling driven gear 12 are fixedly mounted through the intermediate shaft 5, with the gear 10 meshing with the gear 9. A tertiary cable-reeling gear 13 and a tertiary cable-laying gear 14 are fixedly mounted through the tertiary shaft 6, with the tertiary cable-reeling gear 13 meshing with the tertiary cable-reeling driven gear 12, and the tertiary cable-laying gear 14 meshing with the cable-laying driven gear 11. An electromagnetic clutch 16 for the cable-reeling end and an electromagnetic clutch 15 for the cable-laying end are also provided on the intermediate shaft 5.

[0035] Specifically, during operation, the motor power is input via the primary shaft 3, and the first stage of reduction is achieved through the meshing of gear 1 (7) and gear 2 (8). Subsequently, the power is transmitted from gear 3 (9) to gear 4 (10) for the second stage of reduction, reaching the intermediate shaft 5. Depending on the operating conditions, the rotational motion of the intermediate shaft 5 can be selectively transmitted to either the take-up driven gear 12 or the release driven gear 11 by controlling the energization of the take-up electromagnetic clutch 16 or the release electromagnetic clutch 15. If the take-up electromagnetic clutch 16 is engaged, the power is transmitted to the third-stage take-up gear 13 via the take-up driven gear 12, and then output via the third-stage shaft 6, creating a high-speed, low-torque operating condition suitable for take-up lifting. If the release electromagnetic clutch 15 is engaged, the power is transmitted to the third-stage release gear 14 via the release driven gear 11, and then output via the third-stage shaft 6, creating a low-speed, high-torque operating condition suitable for release lowering. A locking design ensures that only one clutch is engaged at any given time, avoiding transmission path conflicts.

[0036] In an optional embodiment, the total length of the primary shaft 3, secondary shaft 4, intermediate shaft 5, and tertiary shaft 6 is 810 mm, and all are made of 45 steel with heat treatment.

[0037] Specifically, the four shafts are designed with equal lengths, which facilitates the symmetrical layout and manufacturing of the housing. The shafts are made of 45 steel and undergo heat treatment to achieve good comprehensive mechanical properties, including high strength and sufficient toughness.

[0038] In an optional embodiment, gear 7 has 18 teeth, gear 8 has 90 teeth and a module of 16mm; gear 9 has 20 teeth, gear 10 has 120 teeth and a module of 16mm; the winding driven gear 12 has 36 teeth, the three-stage winding gear 13 has 100 teeth and a module of 16mm; the unwinding driven gear 11 has 20 teeth, the three-stage unwinding gear 14 has 116 teeth and a module of 16mm.

[0039] Specifically, the number of teeth in each gear set is precisely matched according to the designed transmission ratio. Gear 7 and gear 8 form the first stage of reduction, and gear 9 and gear 10 form the second stage of reduction, together forming a fixed total transmission ratio for the first two stages.

[0040] In an optional embodiment, both the take-up electromagnetic clutch 16 and the release electromagnetic clutch 15 are magnetically attracted electromagnetic clutches with a rated torque ≥25kN・m. They are connected to the intermediate shaft 5 via a spline connection. The size of the clutch driving end is 85×42mm, the size of the driven end is 80×28mm, and the engagement gap is 2mm.

[0041] Specifically, the magnetic electromagnetic clutch features fast response and convenient control. A rated torque of ≥25kN·m ensures reliable transmission of the system's maximum operating torque. The spline connection ensures circumferential positioning accuracy and reliable torque transmission between the clutch and the intermediate shaft 5. The preset 2mm engagement gap is an optimized value, guaranteeing sufficient clutch travel for rapid and reliable disengagement and engagement, while also facilitating smooth control of the engagement process and reducing impact.

[0042] In an optional embodiment, an isolation shoulder with a diameter of 190 mm is provided on the intermediate shaft 5 between the electromagnetic clutch 16 at the cable take-up end and the electromagnetic clutch 15 at the cable release end, in order to mechanically prevent collision interference between the dual clutches during gear shifting.

[0043] Specifically, the shoulder spatially restricts the axial position of the two clutches, ensuring that even in extreme cases where other interlocking measures fail, the mechanical structure ensures that the two clutches cannot collide axially, providing another layer of reliable safety for gear shifting operations.

[0044] In an optional embodiment, the two ends of the third-stage shaft 6 are respectively provided with self-aligning roller bearings and deep groove ball bearings, and the two ends of the intermediate shaft 5 are provided with deep groove ball bearings. The cable take-up driven gear 12 and the cable release driven gear 11 are respectively supported on the intermediate shaft 5 by double deep groove ball bearings.

[0045] Specifically, deep groove ball bearings are used at both ends of the intermediate shaft 5, which mainly bear radial loads. The cable winding driven gear 12 and the cable unwinding driven gear 11 are supported on the intermediate shaft 5 by their respective two deep groove ball bearings in a "cantilever" configuration. This "hollow shaft" structure design allows the gears to rotate freely on the intermediate shaft 5, and they only rotate with the shaft when the corresponding clutch is engaged, which is the key to realizing the switching of the transmission path.

[0046] A dual-transmission ratio switching gearbox with a dual-transmission shifting path, applicable to a dual-transmission ratio switching gearbox, includes the following steps:

[0047] Step 1: The control unit is powered on and collects the system status, including clutch position, motor speed, and load sensor signals. It determines whether the current requirement is cable winding or cable unwinding. If it needs to start from a standby state, the motor is controlled to enter standby mode, at which time the motor idles at low speed or maintains zero torque. If it needs to switch between cable winding and unwinding, the subsequent gear shifting process is executed.

[0048] Step 2: If it is a gear shifting operation, first control the electromagnetic clutch coil on the currently engaged side to de-energize, the electromagnetic force disappears, and under the action of the separation spring, the clutch driving end and driven end separate, with a response time ≤0.23s. At the same time, control the motor to adjust the speed: if switching from cable take-up to cable release, actively reduce the motor speed from the rated speed to the target speed, so that the speed of the cable release driven gear 11 that is about to engage on the intermediate shaft 5 is close to the output speed of the motor after the first two stages of reduction, so as to reduce the meshing impact;

[0049] Step 3: In terms of electrical control, the interlock relay ensures that the original clutch is completely de-energized and the status feedback is "disengaged". The control system sends a pre-position signal to the target clutch, and the coil is ready to be energized.

[0050] Step 4: The target clutch coil is energized, generating an electromagnetic attraction force of ≥1820N, which overcomes the release spring force and quickly closes within the set engagement gap of 2mm, with a response time ≤0.32s. The clutch driving end is rigidly connected to the intermediate shaft 5, and the driven end is locked to the corresponding cable take-up driven gear 12 or cable release driven gear 11 via a flat key, thereby establishing a complete power transmission path.

[0051] S1: Cable winding path: Motor → Primary shaft 3, Gear 1 7 → Secondary shaft 4, Gear 2 8, Gear 3 9 → Intermediate shaft 5, Gear 4 10 → Cable winding end electromagnetic clutch 16 → Cable winding driven gear 12 → Third stage cable winding gear 13 → Drum;

[0052] S2: Cable release path: Motor → Primary shaft 3, Gear 1 7 → Secondary shaft 4, Gear 2 8, Gear 3 9 → Intermediate shaft 5, Gear 4 10 → Cable release end electromagnetic clutch 15 → Cable release driven gear 11 → Third stage cable release gear 14 → Drum;

[0053] Step 5: After the clutch is fully engaged, the control system sends torque and speed commands to the motor according to the target operating conditions to smoothly apply the load. At the same time, the monitoring system collects data from vibration sensors and temperature sensors in real time, as well as feedback on motor current and clutch status, to ensure that there is no abnormal vibration, excessive temperature rise or electrical fault during gear shifting.

[0054] Step 6: The system enters steady-state operation, maintains the target transmission ratio, and the electrical interlock relay keeps the power supply circuit of the non-working side clutch disconnected to prevent both clutches from engaging simultaneously.

[0055] Step 7: When the system has been running stably under the target operating conditions for a set time or has met specific operating parameters, the control unit determines that the shift operation is complete and sends a "successful shift" signal and the current working mode signal, such as cable winding or cable unwinding, to the superior system or operating interface.

[0056] Finally, it should be noted that the above descriptions are merely preferred embodiments of the present invention and are not intended to limit the present invention. Although the present invention has been described in detail with reference to the foregoing embodiments, those skilled in the art can still modify the technical solutions described in the foregoing embodiments or make equivalent substitutions for some of the technical features. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the protection scope of the present invention.

Claims

1. A dual-ratio switching gearbox, characterized in that: It includes a lower housing (1) and an upper housing (2), and the lower housing (1) and the upper housing (2) are equipped with a primary shaft (3), a secondary shaft (4), an intermediate shaft (5) and a tertiary shaft (6). Gear 1 (7) is fixedly installed through the primary shaft (3). Gear 2 (8) and Gear 3 (9) are fixedly installed through the secondary shaft (4). Gear 3 (9) is located below Gear 2 (8). Gear 2 (8) meshes with Gear 1 (7). Gear 4 (10), cable release driven gear (11), and cable take-up driven gear (12) are fixedly installed through the intermediate shaft (5). Gear 4 (10) meshes with Gear 3 (9). A third-stage cable take-up gear (13) and a third-stage cable release gear (14) are fixedly installed through the tertiary shaft (6). The third-stage cable take-up gear (13) meshes with the cable take-up driven gear (12). The third-stage cable release gear (14) meshes with the cable release driven gear (11). The intermediate shaft (5) is also provided with a cable take-up end electromagnetic clutch (16) and a cable release end electromagnetic clutch (15).

2. The dual transmission ratio switching gearbox according to claim 1, characterized in that: The total length of the primary shaft (3), secondary shaft (4), intermediate shaft (5) and tertiary shaft (6) is 810 mm, and all of them are made of 45 steel with heat treatment.

3. The dual transmission ratio switching gearbox according to claim 1, characterized in that: The gear 1 (7) has 18 teeth, the gear 2 (8) has 90 teeth and a module of 16mm; the gear 3 (9) has 20 teeth, the gear 4 (10) has 120 teeth and a module of 16mm; the cable take-up driven gear (12) has 36 teeth, the three-stage cable take-up gear (13) has 100 teeth and a module of 16mm; the cable release driven gear (11) has 20 teeth, the three-stage cable release gear (14) has 116 teeth and a module of 16mm.

4. The dual transmission ratio switching gearbox according to claim 1, characterized in that: The electromagnetic clutch (16) at the cable take-up end and the electromagnetic clutch (15) at the cable release end are both magnetically attracted electromagnetic clutches with a rated torque ≥25kN・m. They are connected to the intermediate shaft (5) using a spline connection. The size of the clutch driving end is 85×42mm, the size of the driven end is 80×28mm, and the engagement gap is 2mm.

5. A dual transmission ratio switching gearbox according to claim 1, characterized in that: The intermediate shaft (5) has an isolation shoulder with a diameter of 190mm between the electromagnetic clutch (16) at the cable take-up end and the electromagnetic clutch (15) at the cable release end, which is used to mechanically prevent the dual clutches from colliding and interfering during gear shifting.

6. The dual transmission ratio switching gearbox according to claim 1, characterized in that: The three-stage shaft (6) is provided with self-aligning roller bearings and deep groove ball bearings at both ends, and the intermediate shaft (5) is provided with deep groove ball bearings at both ends. The cable winding driven gear (12) and the cable unwinding driven gear (11) are supported on the intermediate shaft (5) by double deep groove ball bearings.

7. A dual-transmission ratio switching gearbox with a dual-transmission shifting path, applicable to any one of claims 1-9 above, characterized in that: Includes the following steps: Step 1: The control unit is powered on and collects the system status, including clutch position, motor speed, and load sensor signals. It determines whether the current requirement is cable winding or cable unwinding. If it needs to start from a standby state, the motor is controlled to enter standby mode, at which time the motor idles at low speed or maintains zero torque. If it needs to switch between cable winding and unwinding, the subsequent gear shifting process is executed. Step 2: If it is a gear shifting operation, first control the current engagement side electromagnetic clutch coil to de-energize, the electromagnetic force disappears, and under the action of the separation spring, the clutch driving end and driven end separate, the response time is ≤0.23s. At the same time, control the motor to adjust the speed: if switching from cable take-up to cable release, actively reduce the motor speed from the rated speed to the target speed, so that the speed of the cable release driven gear (11) that is about to engage on the intermediate shaft (5) is close to the output speed of the motor after the first two stages of deceleration, so as to reduce the meshing impact; Step 3: In terms of electrical control, the interlock relay ensures that the original clutch is completely de-energized and the status feedback is "disengaged". The control system sends a pre-position signal to the target clutch, and the coil is ready to be energized. Step 4: The target clutch coil is energized, generating an electromagnetic attraction force of ≥1820N, which overcomes the separation spring force and quickly closes within the set engagement gap of 2mm, with a response time ≤0.32s. The clutch driving end is rigidly connected to the intermediate shaft (5), and the driven end is locked to the corresponding cable winding driven gear (12) or cable unwinding driven gear (11) via a flat key, thereby establishing a complete power transmission path: S1: Cable winding path: motor → primary shaft (3), gear one (7) → secondary shaft (4), gear two (8), gear three (9) → intermediate shaft (5), gear four (10) → cable winding end electromagnetic clutch (16) → cable winding driven gear (12) → third stage cable winding gear (13) → drum; S2: Cable laying path: motor → primary shaft (3), gear one (7) → secondary shaft (4), gear two (8), gear three (9) → intermediate shaft (5), gear four (10) → cable laying end electromagnetic clutch (15) → cable laying driven gear (11) → third stage cable laying gear (14) → drum; Step 5: After the clutch is fully engaged, the control system sends torque and speed commands to the motor according to the target operating conditions to smoothly apply the load. At the same time, the monitoring system collects data from vibration sensors and temperature sensors in real time, as well as feedback on motor current and clutch status, to ensure that there is no abnormal vibration, excessive temperature rise or electrical fault during gear shifting. Step 6: The system enters steady-state operation, maintains the target transmission ratio, and the electrical interlock relay keeps the power supply circuit of the non-working side clutch disconnected to prevent both clutches from engaging simultaneously. Step 7: When the system has been running stably under the target operating conditions for a set time or has met specific operating parameters, the control unit determines that the shift operation is complete and sends a "successful shift" signal and the current working mode signal, such as cable winding or cable unwinding, to the superior system or operating interface.

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