Hoisting equipment applied to aero-engine pulsation production line

Abstract

The invention provides hoisting equipment applied to an aero-engine pulsation production line. The hoisting equipment is used for driving an aero-engine to do linear motion in the first direction and the second direction and rotate around the axis of the aero-engine. The first supporting mechanism comprises a supporting frame and anti-collision supports connected to the two ends of the supporting frame in the first direction. The walking mechanism comprises a driving walking assembly and a driven walking assembly which are fixedly connected with the supporting frame and used for being in sliding connection with the guide rail so as to drive the first supporting mechanism to move in the first direction. The second supporting mechanism comprises a lifting frame and an arc-shaped frame, the lifting frame is slidably connected with the supporting frame, projection parts of the lifting frame and the supporting frame in the second direction are overlapped, and the arc-shaped frame is fixedly connected with the lifting frame; the lifting mechanism comprises a lifting driving assembly with multi-stage physical braking; the rotating mechanism comprises a driving rotating assembly and a main connecting assembly, the main connecting assembly is used for being connected with the aero-engine, and the driving rotating assembly is connected with the arc-shaped frame and used for driving the aero-engine to rotate.

Description

Technical Field

[0001] This application relates to the field of aero-engine assembly technology, and in particular to a hoisting device applied to an aero-engine pulse production line. Background Technology

[0002] Aero engines are characterized by their high value and large size, placing extremely high demands on the hoisting, transfer, and assembly of large components and the entire engine within their pulsed assembly lines. Existing engine assembly hoisting systems typically handle basic vertical lifting and horizontal transport functions, often employing traditional cranes or general-purpose AGVs. However, with the increasing precision required for aero engine assembly and the stringent safety requirements for high-value components, traditional hoisting equipment is showing its inadequacies in load-bearing capacity, motion stability, and coordination with other assembly tools. Current main hoists or transport vehicles often have relatively simple safety designs, particularly in fall protection for vertical lifting mechanisms, relying heavily on motor brakes or single mechanical brakes. When handling engine components weighing several tons for extended periods of time, including hovering or precision attitude adjustments, the lack of multiple redundant physical locking mechanisms in extreme situations such as screw breakage, control system failure, or power outages can easily lead to catastrophic consequences such as load stall and fall. Furthermore, during engine assembly, in addition to conventional three-dimensional movement, the workpiece needs to be rolled around its axis to accommodate installation requirements at different angles. However, existing linear or gantry-type lifting structures struggle to achieve large-angle, high-rigidity rolling adjustments while maintaining a suspended state. Moreover, in multi-point support configurations, the coordinated motion control between the main lifting point and auxiliary support points is complex, easily leading to additional destructive stress on the engine casing due to asynchronous movement. How to solve these problems is a question that those skilled in the art need to consider. Summary of the Invention

[0003] To address the problems in the prior art, this application provides a hoisting device for use in aero-engine pulse production lines.

[0004] This application provides a hoisting device for an aero-engine pulse production line, used at least to drive the aero-engine to move linearly along a first direction and a second direction, and to drive the aero-engine to rotate around its own axis. The hoisting device includes a first support mechanism, a traveling mechanism, a second support mechanism, a lifting mechanism, and a rotating mechanism. The first support mechanism includes a support frame and a collision avoidance bracket, the collision avoidance bracket being connected to both ends of the support frame along the first direction. The traveling mechanism includes an active traveling component and a driven traveling component, both fixedly connected to the support frame and configured to slide along the guide rails of the aero-engine pulse production line, used to drive the first support mechanism to move along the first direction. The second support mechanism includes a lifting frame and an arc-shaped frame, the lifting frame being slidably connected to the support frame with their projections overlapping along the second direction, and the arc-shaped frame being fixedly connected to the lifting frame. The lifting mechanism includes a lifting guide assembly and a lifting drive assembly. The lifting frame and the support frame are slidably connected in a second direction via the lifting guide assembly. The driving part of the lifting drive assembly is connected to the support frame, and its driven part is connected to the lifting frame. It is used to drive the lifting frame to move the arc-shaped frame relative to the first support mechanism in a second direction. The lifting drive assembly has multi-stage physical braking. The rotating mechanism includes an active rotating assembly and a main connecting assembly. The main connecting assembly is fixedly connected to the end of the active rotating assembly and is used to connect the aero-engine. The active rotating assembly is connected to the arc-shaped frame and is used to drive the aero-engine to rotate around its own axis.

[0005] Understandably, the hoisting equipment provided in this application separates the fixed platform from the moving platform by setting up a first support mechanism and a second support mechanism; and through the coordinated action of the traveling mechanism, the lifting mechanism, and the rotating mechanism, the hoisting equipment has the ability to rotate along a first direction, a second direction, and around its own axis. The lifting drive assembly has multi-stage physical braking, which means that the braking system is redundant. When one set of brakes fails, the other sets can still provide braking force, thereby reducing the risk of the load falling due to the failure of a single braking point. At the same time, the rotating mechanism is set on the liftable second support mechanism, enabling the hoisting equipment to perform roll operations on the aero-engine in a suspended state, providing a feasible solution to the problem that existing hoisting equipment is unable to achieve large-angle, high-rigidity roll attitude adjustment in suspension.

[0006] In one embodiment, the support frame includes a first crossbar component and two support components. The two support components are spaced apart along a third direction perpendicular to the first direction. The first crossbar components are connected to the two support components at their respective ends along the third direction. Multiple anti-collision brackets are provided, with each support component connected to an anti-collision bracket at its respective ends along the first direction. The anti-collision brackets extend along the first direction.

[0007] Understandably, the support frame consists of two support components and a first crossbar component, forming a stable base with a relatively large width (along the third direction). This structure helps to distribute the load and resist the torque generated by the lifting equipment during movement, providing a foundation for the operational stability of the lifting equipment. Furthermore, anti-collision brackets extending along the first direction are connected to both the front and rear ends of the support components. These anti-collision brackets form the outermost profile of the lifting equipment in the first direction, serving as physical buffers and protection.

[0008] In one embodiment, the lifting frame includes an upper frame, a side frame, and a lower frame. The upper frame and the lower frame are respectively connected to opposite sides of the side frame along a second direction. The upper frame is located above the support frame along the second direction. The side frame is slidably connected to the support frame via a lifting guide assembly. The arc-shaped frame is fixedly connected to the lower frame and is located on the side of the lower frame away from the support frame along the second direction.

[0009] Understandably, the upper frame is positioned above the support frame to allow the upper frame and the support frame to cross and support each other in the extreme case of the second support mechanism falling, thus preventing the fall; the side frame mainly undertakes the sliding connection and guiding function with the support frame; while the lower frame serves as the main load-bearing platform for fixing the curved frame.

[0010] In one embodiment, the second support mechanism further includes at least two sets of hangers and multiple hook assemblies; the two sets of hangers are located on both sides of the lower frame along a first direction and are respectively connected to the lower frame; the hangers extend along the first direction. Each hook assembly includes a hook sliding component and a hook body. Each hook sliding component is connected to a hanger, and each hook body is slidably connected to a hanger through a hook sliding component, for adjusting the position of the hook body relative to the hanger along the first direction. The lower part of the hook body along a second direction is provided with a hook for connecting an aircraft engine.

[0011] Understandably, adding hangers on both sides of the lower frame provides auxiliary lifting points for the lifting equipment, in addition to the main lifting point (provided by the rotating mechanism). The presence of these hangers expands the lifting capacity and application scenarios of the equipment; for example, it can be used to suspend moving tooling or provide multi-point support for the engine in certain specific processes. The hook body can be adjusted in position along the first direction via the hook sliding component, allowing the position of the auxiliary lifting points to be flexibly changed to adapt to the preset lifting point positions on engines of different models or in different assembly states, enhancing the versatility and ease of operation of the lifting equipment.

[0012] In one embodiment, the lifting mechanism further includes a lifting position detection component, which includes a position detection sensor and a trigger. The position detection sensor is fixedly connected to the support frame, and the trigger is fixedly connected to the lifting frame and can move with the lifting frame along a second direction. The trigger is slidably disposed relative to the position detection sensor along the second direction, and is used to trigger the position detection sensor to generate a position signal when the lifting frame moves to the lifting limit position. The lifting mechanism also includes a lifting parking pin, which is fixedly connected to the support frame. The lifting frame includes a plurality of inserts spaced apart along the second direction, which are used for the lifting parking pin to be inserted into to lock the lifting frame and the support frame.

[0013] Understandably, the positioning sensor is fixed, while the trigger moves with the lifting frame. When the lifting frame reaches its travel limit, the trigger activates the sensor. Upon receiving the positioning signal, the control system stops driving, preventing damage to the equipment structure. After lifting to the predetermined position (determined by the position of the locking block), the lifting parking pin can be inserted into the locking block, rigidly locking the lifting frame to the support frame. This allows for long-term, highly stable height maintenance, improving safety and energy efficiency.

[0014] In one embodiment, the lifting drive assembly includes a lifting drive component, a shaft-end brake, and a linear brake component, both extending along a second direction. The driving portion of the lifting drive component is connected to a support frame, and its driven portion is connected to the lifting frame. The driving portion of the lifting drive component is a drive motor with a braking mechanism, and the driven portion is a lead screw. The shaft-end brake is connected to the driving portion of the lifting drive component and is used to brake the driven portion of the lifting drive component. The linear brake component is connected to both the support frame and the lifting frame, and is used to brake both the support frame and the lifting frame.

[0015] Understandably, the lifting drive assembly has multiple braking systems. The first layer is the braking mechanism integrated into the drive motor within the lifting drive assembly, which is standard power braking. The second layer is the shaft-end brake, which acts on the drive shaft, providing the first layer of redundant braking for the power transmission chain. The third layer is the linear braking component, which acts directly between the support frame and the lifting frame (e.g., on the guide rail). Therefore, even in extreme cases of complete transmission chain failure, such as a broken lead screw, the linear braking component can still function, thus forming a functionally heterogeneous, deeply redundant safety system that significantly improves the reliability of fall protection.

[0016] In one embodiment, the arc-shaped frame has a rotation guide groove, which is recessed towards the lifting frame along the second direction and is arc-shaped. The active rotation component includes a rotation transmission component and a rotation drive component. The rotation transmission component is slidably disposed in the rotation guide groove, and the rotation drive component is disposed in the arc-shaped frame. The rotation drive component is drivenly connected to the rotation transmission component to drive the rotation transmission component to rotate circumferentially.

[0017] Understandably, the arc-shaped rotation guide groove on the arc frame guides the rotation mechanism. The rotating component is constrained to move within this rotation guide groove, and its rotation center and radius are determined by the geometry of the rotation guide groove to achieve smooth and stable rotation of the load around a fixed axis. In one embodiment, the rotary transmission component includes an integrally connected arc-shaped body and a transmission gear ring. The arc-shaped body has an annular cross-section, and the transmission gear ring is connected to the arc-shaped body and protrudes relative to the upper wall of the arc-shaped body along a second direction, extending in an arc shape. The end of the arc-shaped body is connected to a main connecting assembly, and the transmission gear ring is driven to connect with the rotary drive component in a meshing manner. The rotary drive component includes a driven rotating drive member and a rotating output member. The rotating drive member is fixedly installed with the arc frame, and the rotating output member is disposed within the rotation guide groove and driven to connect with the transmission gear ring.

[0018] In one embodiment, the transmission gear ring has multiple spaced-apart arc-shaped toothed grooves on the same side away from the arc-shaped body, with adjacent arc-shaped toothed grooves separated by toothed pillars. The rotary output component includes a fixed plate and multiple meshing cylinders. The fixed plate is connected to the driving end of the rotary drive component and is configured to be driven to rotate. The multiple meshing cylinders are evenly spaced around the rotation axis of the rotary output component. A single arc-shaped toothed groove is used to accommodate one meshing cylinder, allowing the transmission gear ring to mesh with the rotary drive component. The active rotation assembly also includes a rotary parking pin, which is fixedly connected to the arc-shaped frame and has a cylindrical pin head. The cylindrical pin head is configured to be driven to extend or retract in a first direction within a rotation guide groove, for extending into the arc-shaped toothed groove to lock the rotary transmission component.

[0019] Understandably, the rotary drive component is a pin / rack transmission consisting of a meshing cylinder and an arc-shaped toothed groove. Compared to traditional involute gears, this cylinder-to-groove contact is multi-point or line contact, resulting in smoother transmission and allowing for smaller meshing clearance (backlash) through precision machining. Small backlash means almost no play when changing the direction of rotation for precise orientation adjustment, thus improving the response speed and final accuracy of angle positioning. The parking pin mechanically locks the rotary transmission component by extending into the arc-shaped toothed groove. This rigid positioning method, independent of the drive motor brake, eliminates the slight elasticity or creep that may exist in the motor brake when maintaining a precise angle for extended periods during assembly operations, providing greater stability and safety in angle holding.

[0020] In one embodiment, the main connecting assembly includes a main load-bearing pin base, a main load-bearing pin fixing seat, and a main load-bearing pin. The main load-bearing pin base is fixedly connected to the arc-shaped main body, the main load-bearing pin fixing seat is connected to the main load-bearing pin base, and the main load-bearing pin is detachably connected to the main load-bearing pin fixing seat. The main load-bearing pin fixing seat includes a fixing part and a detachable part. The fixing part is fixedly connected to the main load-bearing pin base, and the detachable part is detachably connected to the fixing part by a plurality of locking nuts. The main load-bearing pin is clamped between the fixing part and the detachable part. The main connecting assembly also includes a plurality of anti-fall pin shafts, the axis of which is parallel to the axis of the main load-bearing pin. The fixing part is fixedly connected to the main load-bearing pin base via the anti-fall pin shafts, and the detachable part is also detachably connected to the main load-bearing pin base via the anti-fall pin shafts.

[0021] Understandably, the main load-bearing pin, as a vulnerable or adaptable component in direct contact with the engine, is easily replaceable for different engine interfaces, or repaired after damage, thus improving the versatility and maintainability of the lifting equipment. The main load-bearing pin mounting base is designed as an openable structure consisting of a fixed part and a detachable part. The detachable part can be opened by removing the locking nut, allowing for easy insertion or removal of the clamped main load-bearing pin. This design simplifies the replacement of the load-bearing pin and improves on-site operational efficiency compared to methods requiring complete disassembly of the mounting base. In this embodiment, an anti-fall pin shaft is added as a second layer of connection protection on top of the locking nut connection. The anti-fall pin shaft connects the detachable part to the fixed part via a pin connection. Its function is to maintain the connection between the detachable part and the fixed part even if all locking nuts loosen or fail, thereby preventing the main load-bearing pin from falling off. This is a redundant safety design used to improve the structural reliability of the main connection interface.

[0022] In one embodiment, the hoisting equipment is further configured to be detachably connected to a rear ring follower tooling, the rear ring follower tooling being spaced apart from the active rotation component along a first direction; the rear ring follower tooling includes a connecting frame and a C-frame, the connecting frame being detachably connected to the hanger of the second support mechanism, the connecting frame being slidably connected to the C-frame, the C-frame being configured to be detachably connected to the end of the aero-engine; the rear ring follower tooling also includes a sensing pin, the sensing pin being connected to both the connecting frame and the C-frame to lock the rear ring follower tooling; the sensing pin is further configured to connect to the unlock detection position of the connecting frame when it is separated from the C-frame, and can be sensed by a second tooling sensor, the second tooling sensor being configured to issue a roll limit release signal when the sensing pin is sensed.

[0023] Understandably, the rear-ring follow-up fixture adds an extra support point to the hoisted aero-engine, effectively suppressing potential deformation and vibration and maintaining the stability of the long workpiece during rolling. Furthermore, the sensing pin has a dual function: in transport or non-operating conditions, it locks the C-frame and connecting frame to prevent swaying; during preparation, the operator must pull out the pin to unlock it and insert it into the unlock detection position, where the second fixture sensor can only detect the pin. The control system is configured to allow the main unit's rolling function to activate upon receiving a signal from the sensor indicating that the rolling limit has been released, thus achieving foolproof protection. Attached Figure Description

[0024] Figure 1 This is a three-dimensional schematic diagram of a hoisting device applied to an aero-engine pulse production line, provided in an embodiment of this application.

[0025] Figure 2 This is a three-dimensional schematic diagram from another angle of the hoisting equipment applied to the pulse production line of aero-engines provided in the embodiments of this application.

[0026] Figure 3 This is a three-dimensional schematic diagram showing the first support mechanism, traveling mechanism, and lifting mechanism of the hoisting equipment applied to the pulse production line of an aero-engine, provided in the embodiments of this application, in a coordinated state.

[0027] Figure 4 This is a three-dimensional schematic diagram showing the second support mechanism, rotating mechanism, and rear ring follower tooling of the hoisting equipment applied to the aero-engine pulse production line provided in the embodiments of this application in a coordinated state.

[0028] Figure 5 yes Figure 1 A magnified view of the corresponding V region.

[0029] Figure 6 yes Figure 1A magnified view of the corresponding VI area.

[0030] Figure 7 yes Figure 1 A magnified view of the corresponding region VII.

[0031] Figure 8 yes Figure 3 A magnified view of the corresponding VIII region.

[0032] Figure 9 yes Figure 1 A magnified view of the corresponding IX region.

[0033] Figure 10 yes Figure 2 A magnified view of the corresponding region X.

[0034] Figure 11 This is a three-dimensional schematic diagram of the rotation mechanism of the hoisting equipment applied to the pulse production line of aero-engines, provided in an embodiment of this application.

[0035] Figure 12 yes Figure 11 A magnified view of the corresponding XII region.

[0036] Figure 13 This is a three-dimensional schematic diagram from another angle of the rotating mechanism of the hoisting equipment applied to the pulse production line of aero-engines provided in the embodiments of this application.

[0037] Figure 14 yes Figure 13 A magnified view of the corresponding XIV region.

[0038] Figure 15 yes Figure 1 A magnified view of the corresponding XV region.

[0039] Figure 16 yes Figure 1 A magnified view of the corresponding XVI region.

[0040] Figure 17 yes Figure 4 A magnified view of the corresponding XVII region.

[0041] Figure 18 This is a side view schematic diagram of a hoisting equipment applied to an aero-engine pulse production line, provided in an embodiment of this application.

[0042] Figure 19 yes Figure 2 A magnified view of the corresponding XIX region.

[0043] Explanation of reference numerals in the attached drawings: 11, First support mechanism; 111, Support frame; 1111, First crossbar component; 1112, Support component; 112, Anti-collision bracket; 113, Distance sensing component; 114, Anti-fall pad; 12. Walking mechanism; 121. Active walking component; 1211. First pulley frame; 1212. First rolling element; 1213. Walking drive component; 12131. Walking drive motor; 12132. Walking drive reducer; 12133. Walking drive gear set; 1214. Dust cover; 122. Driven walking component; 1221. Second pulley frame; 1222. Second rolling element; 1223. Walking parking pin; 123. First position code reader; 124. Electrical signal interaction component; 13. Second support mechanism; 131. Lifting frame; 1311. Upper frame; 1312. Side frame; 1313. Lower frame; 1314. Insert block; 132. Arc-shaped frame; 1321. Rotation guide groove; 133. Hanger; 1331. Hanging rod; 134. Hook assembly; 1341. Hook sliding component; 1342. Hook body; 13421. Hook part; 135. Auxiliary tie rod; 136. Anti-fall rod; 137. Rotation guide assembly; 1371. First guide wheel; 1372. Second guide wheel; 14. Lifting mechanism; 141. Lifting guide assembly; 1411. Slide rail; 1412. Slider; 142. Lifting drive assembly; 1421. Lifting drive component; 1422. Shaft end brake; 1423. Linear brake component; 143. Lifting position detection assembly; 1431. Position detection sensor; 1432. Trigger; 144. Lifting parking pin; 15. Rotating mechanism; 151. Active rotating assembly; 1510. Rotary transmission component; 1511. Arc-shaped main body; 1512. Transmission gear ring; 15121. Arc-shaped tooth groove; 15122. Tooth column; 1513. Rotary drive component; 15131. Rotary drive element; 15132. Rotary output element; 15133. Fixing plate; 15134. Meshing cylinder; 1514. Rotating parking pin; 15141. Cylindrical pin head; 152. Main connecting assembly; 1521. Main load-bearing pin base; 1522. Main load-bearing pin fixing seat; 15221. Fixing part; 15222. Detachable part; 1523. Main load-bearing pin; 1524. Locking nut; 1525. Anti-fall pin shaft; 1526. Multi-dimensional force sensor; 16. Rear ring follower fixture; 161. Connecting bracket; 1611. Connecting pin; 162. C-shaped bracket; 163. Induction pin; 164. First fixture sensor; 165. Second fixture sensor; X, first direction; Z, second direction; Y, third direction. Detailed Implementation

[0044] The following is in conjunction with the appendix Figures 1 to 19 This application will be described in further detail below.

[0045] The technical solutions in the embodiments of this application will be further described in detail below with reference to the accompanying drawings. The described embodiments are only possible technical implementations of this application, but are not limited thereto. Other embodiments obtained by those skilled in the art in conjunction with the embodiments of this application without creative effort are also within the protection scope of this application.

[0046] Further integration Figures 1 to 4 As shown, in one embodiment, this application provides a hoisting device for an aero-engine pulse production line, used at least to drive the aero-engine to move linearly along a first direction X and a second direction Z, and to drive the aero-engine to rotate around its own axis. The hoisting device includes a first support mechanism 11, a traveling mechanism 12, a second support mechanism 13, a lifting mechanism 14, and a rotating mechanism 15. The first support mechanism 11 includes a support frame 111 and a collision avoidance bracket 112, the collision avoidance bracket 112 being connected to both ends of the support frame 111 along the first direction X. The traveling mechanism 12 includes an active traveling component 121 and a driven traveling component 122, both of which are fixedly connected to the support frame 111 and configured to slide along the guide rail of the aero-engine pulse production line, used to drive the first support mechanism 11 to move along the first direction X. The second support mechanism 13 includes a lifting frame 131 and an arc-shaped frame 132. The lifting frame 131 is slidably connected to the support frame 111, and their projections along the second direction Z overlap. The arc-shaped frame 132 is fixedly connected to the lifting frame 131. The lifting mechanism 14 includes a lifting guide assembly 141 and a lifting drive assembly 142. The lifting frame 131 and the support frame 111 are slidably connected along the second direction Z via the lifting guide assembly 141. The driving part of the lifting drive assembly 142 is connected to the support frame 111, and its driven part is connected to the lifting frame 131. It is used to drive the lifting frame 131 to move the arc-shaped frame 132 relative to the first support mechanism 11 along the second direction Z. The lifting drive assembly 142 has multi-stage physical braking. The rotating mechanism 15 includes an active rotating assembly 151 and a main connecting assembly 152. The main connecting assembly 152 is fixedly connected to the end of the active rotating assembly 151 and is used to connect the aero-engine. The active rotating assembly 151 is connected to the arc-shaped frame 132 and is used to drive the aero-engine to rotate around its own axis.

[0047] In this embodiment, the first support mechanism 11 serves as the basic frame of the hoisting equipment's traveling unit, providing a load-bearing platform for the installation of other mechanisms. The traveling mechanism 12 is mounted on the first support mechanism 11 and cooperates with the overhead guide rails of the production line to achieve long-distance transportation of the hoisting equipment in the first direction X (e.g., the horizontal X-axis direction). The second support mechanism 13 serves as an attitude adjustment unit, capable of lifting and lowering relative to the first support mechanism 11 in the second direction Z (e.g., the vertical Z-axis direction). The rotating mechanism 15 is integrated into the second support mechanism 13 and is used to achieve roll attitude adjustment of the aero-engine around its own axis (e.g., the A-axis). The maximum load-bearing capacity of the entire hoisting equipment is not less than 4.5 tons, and the main structure is made of Q355 high-strength steel.

[0048] Understandably, the hoisting equipment provided in this application separates the fixed platform from the moving platform by setting up a first support mechanism 11 and a second support mechanism 13; and through the coordinated action of the traveling mechanism 12, the lifting mechanism 14, and the rotating mechanism 15, the hoisting equipment has the ability to rotate along the first direction X, the second direction Z, and around its own axis. The lifting drive assembly 142 explicitly includes multi-stage physical braking, which means that the braking system has redundancy. When one set of brakes fails, the other sets can still provide braking force, thereby reducing the risk of the load falling due to the failure of a single braking point. At the same time, the rotating mechanism 15 is set on the liftable second support mechanism 13, enabling the hoisting equipment to perform roll operations on the aero-engine in a suspended state, providing a feasible solution to the problem that existing hoisting equipment is unable to achieve large-angle, high-rigidity roll attitude adjustment in suspension.

[0049] It should be explained that the aircraft engine mentioned is not limited to a complete aircraft engine as a whole, but can also be a part of the aircraft engine, such as the main unit or fan unit of the aircraft engine.

[0050] Further integration Figure 3 As shown, in one embodiment, the support frame 111 includes a first crossbar component 1111 and two support components 1112. The two support components 1112 are spaced apart along a third direction Y perpendicular to the first direction X. The two ends of the first crossbar components 1111, spaced apart along the third direction Y, are respectively connected to the two support components 1112. There are multiple anti-collision brackets 112, and each support component 1112 is connected to an anti-collision bracket 112 at spaced apart along the first direction X. The anti-collision brackets 112 extend along the first direction X.

[0051] In this embodiment, the support frame 111 has an overall "H" shape, with two support components 1112 arranged in parallel and rigidly connected by the first crossbar component 1111, forming a stable main frame for the walking unit with sufficient torsional stiffness. The anti-collision brackets 112 are fixed to the front and rear ends of each support component 1112 by bolts or welding, and their ends can be provided with high-strength rubber or other buffer materials to absorb collision energy.

[0052] Understandably, the support frame 111 consists of two support components 1112 and a first crossbar component 1111, forming a stable base with a relatively large width (along the third direction Y). This structure helps to distribute the load and resist the torque generated by the lifting equipment during movement, providing a foundation for the operational stability of the lifting equipment. Furthermore, anti-collision brackets 112 extending along the first direction X are connected to both the front and rear ends of the support components 1112. These anti-collision brackets 112 form the outermost profile of the lifting equipment in the first direction X, serving as physical buffers and protection.

[0053] In one embodiment, the first support mechanism 11 further includes a plurality of anti-fall pads 114, which are disposed on the side of the first crossbar component 1111 away from the arc-shaped frame 132 along the second direction Z. The lifting frame 131 overlaps with the projection portion of the anti-fall pads 114 along the second direction Z.

[0054] In this embodiment, the anti-fall pad 114 is a rubber block, which is fixed to the upper surface of the first crossbar component 1111 by bolts, serving as the final physical hard limit of the lifting mechanism 14 when all active safety measures fail.

[0055] Understandably, the anti-fall pad 114 is mounted on the fixed first crossbar component 1111, and its position overlaps with the vertical projection of the moving lifting frame 131. In the extreme case where all active braking measures of the lifting system fail, the descending lifting frame 131 will come into rigid contact with the anti-fall pad 114 and be blocked.

[0056] In one embodiment, the sum of the lengths of the integrally connected support member 1112 and two anti-collision brackets 112 along the first direction X is configured to be greater than the length of the aircraft engine being hoisted by the hoisting equipment along the first direction X.

[0057] Understandably, the combined length of the support component 1112 and the anti-collision bracket 112 is greater than the length of the aircraft engine. This ensures that, in the event of a collision while the hoisting equipment is moving along the first direction X, the anti-collision bracket 112 of the hoisting equipment will contact the obstacle before the aircraft engine itself. By utilizing the physical dimensions of the structure itself, a layer of pre-emptive physical protection is provided for the high-value workpiece being hoisted, reducing the risk of engine damage due to accidental collisions during movement.

[0058] In one embodiment, the first support mechanism 11 further includes a distance sensing component 113 (such as...). Figure 9 As shown), the distance sensing component 113 is disposed on the support component 1112 and / or the anti-collision bracket 112, and is used to sense the distance between the first support mechanism 11 and adjacent obstacles on the aero-engine production line.

[0059] In this embodiment, the distance sensing component 113 may include a laser rangefinder and an obstacle avoidance radar. The laser rangefinder is mounted on the front and rear anti-collision brackets 112 to accurately measure the distance to adjacent hoisting equipment, ensuring a minimum distance of 2 meters. The obstacle avoidance radar is also mounted at both ends and can detect obstacles over a wider range along the path, such as obstacles within a 5x3x3 meter space, providing warnings and emergency stop signals to the control system.

[0060] Understandably, a distance sensing component 113 is added to the physical protection of the anti-collision bracket 112. By actively detecting and quantifying the distance to obstacles using the distance sensing component 113, it can provide early warning information to the control system of the hoisting equipment. Upon receiving a signal indicating that the distance is too close, the control system can execute preset logic such as deceleration or stopping, enabling the hoisting equipment to actively avoid obstacles and further improving operational safety.

[0061] Further integration Figure 5 and Figure 6 As shown, in one embodiment, the walking mechanism 12 includes two active walking components 121 and two passive walking components 122. Each support component 1112 is fixedly connected to one active walking component 121 and one passive walking component 122. The active walking component 121 and the passive walking component 122 are located on the side of the support component 1112 away from the arc-shaped frame 132 along the second direction Z.

[0062] In this embodiment, both the active walking component 121 and the passive walking component 122 are mounted on the upper surface of the support component 1112 and are rigidly connected to the support component 1112 via a mounting base to cooperate with the overhead guide rail located above the production line.

[0063] Understandably, the two active and two driven traveling components 122 are symmetrically distributed on the two support members 1112, employing a four-point support and dual-sided drive layout. Compared to single-sided drive, the four-point support and dual-sided drive layout provides more balanced traction and reduces the possibility of yaw during the start-up or braking of the lifting equipment. Placing the traveling components above the support member 1112 allows for close coordination with the production line track located above, while also avoiding interference with the aircraft engine located below the support member 1112.

[0064] In one embodiment, the walking mechanism 12 includes two active walking components 121 and two passive walking components 122, with each support member 1112 connected to one active walking component 121 and one passive walking component 122. The two active walking components 121 are spaced apart along a third direction Y and arranged side by side along a first direction X, while the other two passive walking components 122 are spaced apart along a third direction Y and arranged side by side along the first direction X.

[0065] In this embodiment, the two active walking components 121 are arranged as the front wheel set, and the two driven walking components 122 are arranged as the rear wheel set. Concentrating the drive unit at one end of the hoisting equipment facilitates centralized arrangement and maintenance of the power system.

[0066] Understandably, the active walking assembly 121 and the driven walking assembly 122 are arranged in pairs along the first direction X, with the drive wheel set and the driven wheel set distributed at both ends (or front and rear) of the lifting equipment. This helps to optimize the axle load distribution and the application of driving force / braking force of the whole vehicle, and has a positive effect on improving the dynamic stability during walking or acceleration and deceleration.

[0067] In one embodiment, the active walking assembly 121 includes a first pulley frame 1211, first rolling elements 1212, and a walking drive component 1213. The first pulley frame 1211 is fixedly connected to the support frame 111, and a plurality of first rolling elements 1212 are rotatably connected to the first pulley frame 1211. The walking drive component 1213 is connected to at least a portion of the first rolling elements 1212 via gear drive, and is used to drive at least a portion of the first rolling elements 1212 to rotate, thereby driving the first pulley frame 1211 to walk along the guide rail.

[0068] In this embodiment, the outer edge of the first rolling element 1212 is wrapped with a non-metallic material, such as polyurethane, to increase the coefficient of friction and protect the guide rail surface. The walking drive component 1213 can achieve multi-level speed control, such as three-speed precise positioning control of 1 mm / s, 5 mm / s, and 30 mm / s in the assembly station, and a maximum speed of 150 mm / s on the no-load return line.

[0069] Understandably, the walking drive component 1213 outputs power and transmits it to the first rolling element 1212 through gear drive. The rotation of the first rolling element 1212 drives the entire first pulley frame 1211 to move along the guide rail.

[0070] In one embodiment, the walking drive component 1213 includes a walking drive motor 12131, a walking drive reducer 12132, and a walking drive gear set 12133. The walking drive gear set 12133 is drivenly connected to at least a portion of the first rolling element 1212, and the walking drive motor 12131 is drivenly connected to the walking drive gear set 12133 via the walking drive reducer 12132. The active walking component 121 also includes a dust cover 1214, which is disposed above the walking drive gear set 12133 and is used to shield the walking drive gear set 12133.

[0071] In this embodiment, the travel drive motor 12131 is a servo motor with a brake module. A lubricating felt gear may also be provided next to the travel drive gear set 12133 for continuous, minute lubrication of the gear set, reducing maintenance frequency. The dust cover 1214 is a metal or engineering plastic housing that covers the gear transmission area to prevent external dust and debris from entering.

[0072] Understandably, the travel drive motor 12131 is connected to the travel drive gear set 12133 via the travel drive reducer 12132. The addition of the reducer can increase the output torque while reducing the output speed, enabling the lifting equipment to start and run smoothly at a lower speed, facilitating precise positioning. The added dust cover 1214 provides physical isolation for the exposed travel drive gear set 12133, reducing the possibility of dust and debris entering the meshing area, which helps maintain transmission accuracy and extend the service life of components.

[0073] In one embodiment, the driven walking assembly 122 includes a second pulley frame 1221, second rolling elements 1222, and a walking parking pin 1223. The second pulley frame 1221 is fixedly connected to the support frame 111, and a plurality of second rolling elements 1222 are rotatably connected to the second pulley frame 1221 for guiding the second pulley frame 1221 to move along the guide rail. The walking parking pin 1223 is fixedly connected to the second pulley frame 1221 and is used to extend the pin to fix the first support mechanism 11 and the guide rail when the hoisting equipment is relatively stationary along the guide rail.

[0074] In this embodiment, the parking latch 1223 is driven by an electromagnetic actuator and can be operated wirelessly via remote control. The extension and retraction states of the latch are detected by a position sensor, and the status signals are fed back to the control system and the on-site audio-visual prompts to ensure that the operator is clearly aware of the locked state.

[0075] Understandably, the frame (first support mechanism 11) is rigidly connected to the guide rail directly via a pin. When long-term precise positioning or parking is required, this mechanical locking method can eliminate the slight displacement caused by possible gaps or elastic deformation in the drive chain, providing higher positioning stability and safety than simply relying on the motor brake.

[0076] In one embodiment, the walking mechanism 12 further includes a first position reader 123 and an electrical signal interaction component 124. The first position reader 123 is connected to the second pulley frame 1221 and is spaced apart from the guide rail, for reading the position of the driven walking component 122 relative to the guide rail; the electrical signal interaction component 124 is connected to the second pulley frame 1221 and is used to slide in contact with an external conductor and perform electrical signal interaction.

[0077] In this embodiment, the first position reader 123 is used to read the position coding strip (e.g., QR code strip or magnetic ruler) laid along the guide rail to obtain the absolute position information of the hoisting equipment. The electrical signal interaction component 124 is specifically a sliding contact line current collector, which provides continuous power supply and stable data communication for the entire hoisting equipment through contact with the sliding contact line guide rail parallel to the production line, without the need for dragging cables.

[0078] Understandably, the inclusion of the first position reader 123 enables the control system of the hoisting equipment to obtain its precise position information on the guide rail in real time. The inclusion of the electrical signal interaction component 124 (such as a sliding contact line) allows the hoisting equipment to achieve continuous power supply and communication without the need for a drag cable.

[0079] Further integration Figure 7 and Figure 8 As shown, in one embodiment, the lifting mechanism 14 includes four sets of lifting guide assemblies 141. Each support member 1112 is connected to two sets of lifting guide assemblies 141, and the two sets of lifting guide assemblies 141 are spaced apart along the first direction X on both sides of the first crossbar member 1111. The lifting guide assemblies 141 are all located on the opposite sides of the two support members 1112 along the third direction Y.

[0080] In this embodiment, four sets of lifting guide components 141 form a rectangular guide frame, which are located at the four corners of the space enclosed by the support frame 111, providing stable and precise vertical movement guidance for the lifting frame 131 and effectively resisting the overturning moment caused by eccentric load.

[0081] Understandably, the four sets of lifting guide components 141 are distributed on the inner side of the two support components 1112 and are spaced apart along the first direction X, providing constraints in multiple directions for the vertical movement of the lifting frame 131. This effectively resists the lateral forces and overturning moments generated by uneven loads or the start and stop of movement, ensuring the stability of the lifting frame 131's posture and the accuracy of its trajectory during the lifting process.

[0082] Further integration Figure 4 As shown, in one embodiment, the lifting frame 131 includes an upper frame 1311, a side frame 1312, and a lower frame 1313. The upper frame 1311 and the lower frame 1313 are respectively connected to the two opposite sides of the side frame 1312 along the second direction Z. The upper frame 1311 is located above the support frame 111 along the second direction Z. The side frame 1312 is slidably connected to the support frame 111 through a lifting guide assembly 141. The arc-shaped frame 132 is fixedly connected to the lower frame 1313 and is located on the side of the lower frame 1313 away from the support frame 111 along the second direction Z.

[0083] Understandably, the lifting frame 131 is a hollow steel structure that is integrally welded or bolted together. The upper frame is located above the support frame 111 and is used to cross-support the upper frame and the support frame 111 in the extreme case of the second support mechanism 13 falling, thus preventing the fall; the side frame 1312 mainly undertakes the sliding connection and guiding function with the support frame 111; while the lower frame 1313 serves as the main load-bearing platform for fixing the arc-shaped frame 132.

[0084] In one embodiment, the second support mechanism 13 further includes at least two sets of hangers 133, which are located on both sides of the lower frame 1313 along the first direction X and are respectively connected to the lower frame 1313. The hangers 133 extend along the first direction X.

[0085] In this embodiment, the suspender 133 is divided into a front suspender and a rear suspender, which are used to connect different units of the aero-engine or to attach the rear ring follower tooling 16, providing flexible multi-point suspension capability.

[0086] Understandably, the addition of hangers 133 on both sides of the lower frame 1313 provides auxiliary lifting points for the lifting equipment in addition to the main lifting point (provided by the rotating mechanism 15). The presence of these hangers 133 expands the lifting capacity and application scenarios of the lifting equipment, for example, it can be used to suspend follow-up tooling, or to provide multi-point support for the engine in certain specific processes.

[0087] In one embodiment, the second support mechanism 13 further includes a plurality of hook assemblies 134, each hook assembly 134 including a hook sliding component 1341 and a hook body 1342. Each hook sliding component 1341 is connected to a hanger 133, and each hook body 1342 is slidably connected to a hanger 133 via a hook sliding component 1341 for adjusting the position of the hook body 1342 relative to the hanger 133 along a first direction X. The lower part of the hook body 1342 along a second direction Z is provided with a hook portion 13421 for connecting an aircraft engine.

[0088] In this embodiment, a linear guide rail is installed on the hanger 133, and the hook sliding component 1341 is a slider structure installed on the guide rail, so that the hook body 1342 can be manually or electrically adjusted along the first direction X to adapt to workpieces with different lifting point spacing.

[0089] Understandably, the hook body 1342 can be adjusted in position along the first direction X through the hook sliding component 1341, so that the position of the auxiliary lifting point can be flexibly changed to adapt to the preset lifting point position on the engine of different models or different assembly states, thereby enhancing the versatility and ease of operation of the lifting equipment.

[0090] In one embodiment, each set of hangers 133 includes two hanger rods 1331, and the second support mechanism 13 includes four hook assemblies 134, each hook assembly 134 being connected to one hanger rod 1331.

[0091] In this embodiment, four independent hook assemblies 134 provide four-point auxiliary support capabilities, which can provide more stable and more evenly distributed load-bearing capacity for large components or the whole machine.

[0092] Understandably, the lifting equipment has four independently adjustable auxiliary lifting points, forming a four-point auxiliary lifting system. Four-point support provides more stable support for large and long workpieces, helping to suppress deformation during lifting.

[0093] In one embodiment, each hanger 133 is connected to the side frame 1312 via an auxiliary tie rod 135. The two ends of the auxiliary tie rod 135 are connected to the upper part of the hanger 133 and the side frame 1312 via pins or bolts, respectively, forming a stable triangular support structure.

[0094] Understandably, by adding an auxiliary tie rod 135 to connect the hanger 133 to the side frame 1312, a stable triangular structure is formed. The addition of the auxiliary tie rod 135 can significantly enhance the hanger 133's ability to resist lateral forces and bending moments, ensuring the stiffness and positional stability of the auxiliary lifting point under load.

[0095] Further integration Figure 7 and Figure 8 As shown, in one embodiment, the lifting guide assembly 141 includes multiple sets of sliding grooves 1411 and sliders 1412 that can slide together. The multiple grooves 1411 are connected to the side frame 1312 and extend along the second direction Z. The multiple sliders 1412 are respectively connected to the support frame 111.

[0096] In this embodiment, the lifting guide assembly 141 is specifically a high-precision heavy-duty roller linear guide. The slide rail 1411 is the guide rail, which is fixed to the side frame 1312 of the lifting frame 131 by bolts; the slider 1412 is fixed to the inner side wall of the support frame 111, and the rolling elements inside it are in rolling contact with the guide rail.

[0097] Understandably, the combination of the slide rail 1411 and the slider 1412 is a mature linear motion guiding solution. The slide rail 1411 provides a precise motion trajectory for the slider 1412, while the rolling or sliding cooperation between the two can achieve low-friction relative motion. By fixing the slide rail 1411 to the moving side frame 1312 and the slider 1412 to the stationary support frame 111, the function of the lifting frame 131 moving smoothly along a fixed trajectory is realized.

[0098] In one embodiment, the lifting mechanism 14 further includes a lifting position detection component 143, which includes a position detection sensor 1431 and a trigger 1432. The position detection sensor 1431 is fixedly connected to the support frame 111, and the trigger 1432 is fixedly connected to the lifting frame 131 and can move with the lifting frame 131 along the second direction Z. The trigger 1432 is slidably disposed relative to the position detection sensor 1431 along the second direction Z, and is used to trigger the position detection sensor 1431 to generate a position signal when the lifting frame 131 moves to the lifting limit position.

[0099] In this embodiment, the position detection sensor 1431 is a limit switch or a proximity switch, which is installed at the upper and lower ends of the lifting stroke, respectively. In addition, the lifting mechanism 14 is also equipped with a magnetic scale, which can provide real-time and continuous feedback on the precise height position of the lifting frame 131 and display it on the display screen of the hoisting equipment.

[0100] Understandably, the positioning sensor 1431 is fixed, while the trigger 1432 moves with the lifting frame 131. When the lifting frame 131 moves to its limit position, the trigger 1432 will activate the sensor. Upon receiving the positioning signal, the control system will stop driving, thus avoiding damage to the equipment structure.

[0101] In one embodiment, the lifting mechanism 14 further includes a lifting parking pin 144, which is fixedly connected to the support frame 111. The lifting frame 131 includes a plurality of inserts 1314 spaced apart along the second direction Z, which are used for inserting the lifting parking pin 144 to lock the lifting frame 131 and the support frame 111.

[0102] In this embodiment, when the lifting frame 131 moves to the highest point, the lifting parking pin 144 is driven by the electromagnetic actuator to extend and insert into the plug 1314 (connection hole) on the lifting frame 131, serving as a physical lock after the lifting mechanism 14 reaches the high position, ensuring safety before long-distance travel.

[0103] Understandably, after the lifting mechanism reaches the predetermined position (determined by the position of the insert block 1314), the lifting parking pin 144 can be inserted into the insert block 1314 to rigidly lock the lifting frame 131 and the support frame 111 together. This enables long-term, highly stable height maintenance, improving safety and energy efficiency.

[0104] Further integration Figure 9 As shown, in one embodiment, the lifting drive assembly 142 includes a lifting drive component 1421, a shaft-end brake 1422, and a linear brake component 1423. Both the lifting drive component 1421 and the linear brake component 1423 extend along a second direction Z. The driving part of the lifting drive component 1421 is connected to the support frame 111, and its driven part is connected to the lifting frame 131. The driving part of the lifting drive component 1421 is a drive motor with a braking mechanism, and the driven part of the lifting drive component 1421 is a lead screw. The shaft-end brake 1422 is connected to the driving part of the lifting drive component 1421 and is used to brake the driven part of the lifting drive component 1421. The linear brake component 1423 is connected to both the support frame 111 and the lifting frame 131 and is used to brake both the support frame 111 and the lifting frame 131.

[0105] Understandably, the lifting drive assembly 142 has multiple braking systems. The first layer is the braking mechanism integrated into the drive motor within the lifting drive assembly 1421, which is standard power braking. The second layer is the shaft-end brake 1422, which acts on the drive shaft, providing the first layer of redundant braking for the power transmission chain. The third layer is the linear brake assembly 1423, which acts directly between the support frame 111 and the lifting frame 131 (e.g., on the guide rail). Therefore, even in extreme cases of complete transmission chain failure, such as screw breakage, the linear brake assembly 1423 can still function, thus forming a functionally heterogeneous, deeply redundant safety system that significantly improves the reliability of fall protection.

[0106] In one embodiment, the lifting mechanism 14 includes two sets of lifting drive assemblies 142, which are spaced apart along a third direction Y and respectively connected between the first support mechanism 11 and the second support mechanism 13. Each set of lifting drive assemblies 142 includes a linear brake component 1423, two lifting drive components 1421, and two shaft end brakes 1422. The two lifting drive components 1421 are spaced apart along a first direction X, and each shaft end brake 1422 cooperates with one lifting drive component 1421. A linear brake component 1423 is disposed between the two lifting drive components 1421 along the first direction X.

[0107] In this embodiment, a total of four lifting screws (i.e., four lifting drive components 1421), four servo motors with holding brakes, four shaft-end brakes 1422, and two linear brake components 1423 are configured. This fully redundant configuration ensures extremely high safety.

[0108] Understandably, by setting the lifting drive components 142 into two groups and symmetrically arranging them, dual-path redundancy of the driving force is achieved. Each group contains two lifting drive components 1421, further distributing the load and increasing drive redundancy. Even if one or more drive components fail, the system can still maintain the load or descend slowly. The linear braking component 1423 is positioned between the two lifting drive components 1421, which helps to apply a more balanced braking force during braking, avoids the generation of yaw torque, and ensures attitude stability during emergency braking.

[0109] Understandably, the multi-stage physical braking includes at least a servo motor with a holding brake, an axle-end brake 1422, and a linear braking component 1423.

[0110] Further integration Figure 4 and Figure 10 As shown, in one embodiment, the arc-shaped frame 132 is provided with a rotation guide groove 1321. The rotation guide groove 1321 is recessed along the second direction Z toward the side of the lifting frame 131 and is arc-shaped.

[0111] In this embodiment, the arc frame 132 is a C-shaped rolling frame, and the rotation guide groove 1321 is formed on the inner edge of the frame by precision machining or wire cutting. Its arc radius and center position determine the rolling center of the aero-engine.

[0112] Understandably, the arc-shaped rotation guide groove 1321 on the arc frame 132 provides guidance for the rotating mechanism 15. The rotating component is constrained to move within the rotation guide groove 1321, and its rotation center and radius are determined by the geometry of the rotation guide groove 1321 to achieve smooth and stable rotation of the load around a fixed axis.

[0113] Further integration Figures 11 to 14 As shown, in one embodiment, the active rotation component 151 includes a rotation transmission component 1510 and a rotation drive component 1513. The rotation transmission component 1510 is slidably disposed in the rotation guide groove 1321, and the rotation drive component 1513 is disposed on the arc-shaped frame 132. The rotation drive component 1513 is drivenly connected to the rotation transmission component 1510 and is used to drive the rotation transmission component 1510 to rotate in a circular motion.

[0114] In this embodiment, the rotary drive component 1513 is driven by a servo motor, which can achieve precise angle and speed control, with a maximum roll speed of 2 degrees / second.

[0115] In one embodiment, the rotary transmission component 1510 includes an integrally connected arc-shaped body 1511 and a transmission gear ring 1512. The arc-shaped body 1511 has an annular cross-section. The transmission gear ring 1512 is connected to the arc-shaped body 1511 and protrudes from the upper wall of the arc-shaped body 1511 along the second direction Z. The transmission gear ring 1512 extends in an arc shape. The end of the arc-shaped body 1511 is connected to the main connecting assembly 152, and the transmission gear ring 1512 is driven connected to the rotary drive component 1513 in an engaging manner.

[0116] Understandably, the rotary transmission component 1510 engages with the rotary drive component 1513 through the transmission gear ring 1512. Compared with friction transmission, it can transmit greater torque, and the transmission ratio is precisely fixed with no relative slippage, enabling precise angle control.

[0117] In one embodiment, the rotary drive component 1513 includes a rotary drive component 15131 and a rotary output component 15132 that are driven together. The rotary drive component 15131 is fixedly disposed with the arc frame 132, and the rotary output component 15132 is disposed inside the rotation guide groove 1321 and drivenly connected with the transmission gear ring 1512.

[0118] In this embodiment, the rotary drive 15131 is a servo motor and a matching reducer, and its output shaft is connected to the rotary output 15132.

[0119] In one embodiment, the transmission gear ring 1512 has multiple spaced arc-shaped toothed grooves 15121 on the same side away from the arc-shaped body 1511, and adjacent arc-shaped toothed grooves 15121 are separated by toothed pillars 15122. The rotary output member 15132 includes a fixed plate 15133 and multiple meshing cylinders 15134. The fixed plate 15133 is connected to the driving end of the rotary drive member 15131 and is configured to be driven to rotate. The multiple meshing cylinders 15134 are evenly spaced around the rotation axis of the rotary output member 15132. A single arc-shaped toothed groove 15121 is used to accommodate one meshing cylinder 15134, so that the transmission gear ring 1512 meshes with the rotary drive member 15131.

[0120] In this embodiment, the meshing cylinder 15134 can be a precision-manufactured carbide roller that can enter and exit the arc-shaped toothed groove 15121 in a rolling manner. The transmission process is extremely smooth and the meshing gap is very small, ensuring high-precision angular positioning.

[0121] Understandably, the rotary drive component 1513 is a pin / rack transmission consisting of a meshing cylinder 15134 and an arc-shaped toothed groove 15121. Compared to traditional involute gears, this cylinder-groove contact is multi-point or line contact, resulting in smooth transmission and allowing for smaller meshing clearance (backlash) through precision machining. For precision orientation adjustment, small backlash means almost no idle travel when changing the direction of rotation, thereby improving the response speed and final accuracy of angular positioning.

[0122] In one embodiment, the active rotation assembly 151 further includes a rotation parking pin 1514, which is fixedly connected to the arcuate frame 132. The rotation parking pin 1514 has a cylindrical pin head 15141. The cylindrical pin head 15141 is configured to be driven to extend or retract in the rotation guide groove 1321 along a first direction X, for extending into the arcuate toothed groove 15121 to lock the rotational transmission component 1510.

[0123] In this embodiment, the rotating parking pin 1514, also known as the angle positioning pin, is driven by an electromagnetic actuator. It can extend at a preset specific angle position (e.g., 0 degrees, ±30 degrees, ±60 degrees) and insert into the arc-shaped toothed groove 15121 of the transmission gear ring 1512, forming a double lock with the motor brake to ensure angular stability in critical processes such as docking.

[0124] Understandably, rotating the parking pin 1514 mechanically locks the rotary transmission component 1510 by inserting it into the arc-shaped toothed groove 15121. This rigid positioning method, independent of the drive motor brake, eliminates the slight elasticity or creep that may exist in the motor brake when assembly operations require maintaining a precise angle for extended periods, providing greater stability and safety in angle holding.

[0125] Understandably, both the rotary drive component 1513 and the rotary parking pin 1514 can cooperate with the arc-shaped tooth groove 15121 of the transmission gear ring 1512, which can achieve high-precision transmission and further realize parking limit, thereby improving safety.

[0126] Further integration Figure 4 and 10 As shown, in one embodiment, the second support mechanism 13 further includes multiple anti-fall rods 136, which are fixedly connected to the arc-shaped frame 132. The anti-fall rods 136 are arranged across the rotation guide groove 1321 along the first direction X, and are used to cooperate with the arc-shaped frame 132 to limit the rotation transmission component 1510 within the rotation guide groove 1321.

[0127] In this embodiment, the fall arrestor 136 is a high-strength steel rod, with multiple rods evenly distributed in the middle area of ​​the arc-shaped frame 132. There is a gap between it and the rotating transmission component 1510, so they do not contact each other during normal operation.

[0128] Understandably, the anti-fall bar 136 spans the opening of the rotation guide groove 1321, thus physically restricting the downward vertical direction of the rotary transmission component 1510. Even in extreme cases (such as when the guide wheel is damaged), the anti-fall bar 136 can prevent the rotary transmission component 1510 from dislodging from the rotation guide groove 1321, providing an additional layer of protection for the structural integrity of the rotating mechanism.

[0129] In one embodiment, the second support mechanism 13 further includes a rotation guide assembly 137, which is rotatably connected to the arc-shaped frame 132 and is used to guide the rotation of the rotation transmission component 1510. The rotation guide assembly 137 includes a plurality of first guide wheels 1371 and a plurality of second guide wheels 1372. The first guide wheels 1371 are embedded in the sidewalls of the arc-shaped frame 132 spaced apart along the first direction X and are used to make rolling contact with the sidewalls of the rotation transmission component 1510 along the first direction X. The plurality of second guide wheels 1372 are arranged intersectingly and spaced apart with a plurality of fall arresting rods 136 and are used to make rolling contact with the bottom wall of the rotation transmission component 1510 along the second direction Z, so that the rotation transmission component 1510 and the fall arresting rods 136 are spaced apart along the second direction Z.

[0130] In this embodiment, the first guide wheel 1371 is a tilting guide wheel used to constrain the lateral position of the rotary transmission component 1510. The second guide wheel 1372 is an auxiliary load-bearing guide wheel, installed close to the anti-fall bar 136, and rolls in contact with the lower surface of the rotary transmission component 1510, sharing part of the load and providing upward support, thereby reducing the friction between the rotary transmission component 1510 and the bottom surface of the rotation guide groove 1321.

[0131] Understandably, the combination of the first guide wheel 1371 and the second guide wheel 1372 provides omnidirectional rolling guidance for the rotary transmission component 1510. By using rolling contact instead of sliding contact, the frictional resistance of the rotary transmission component 1510 during movement can be significantly reduced, resulting in smoother movement and ensuring high precision in rotary motion.

[0132] In one embodiment, the rotation angle of the arc-shaped body 1511 relative to the arc-shaped frame 132 ranges from -60° to +60°.

[0133] In this embodiment, by providing a mechanical limiting groove at the end of the arc-shaped body 1511 that cooperates with the fall arrestor 136, and by setting a software limit in the control system, the rotation angle is ensured not to exceed this range.

[0134] Understandably, limiting the rotation angle range to ±60° allows the lifting equipment to meet the process requirements of large-scale flipping or tilting of workpieces in aero-engine assembly, and it has better process adaptability compared to lifting equipment with limited rotation angle.

[0135] Further integration Figures 15 to 17 As shown, in one embodiment, the rotating mechanism 15 includes two main connecting components 152, which are respectively disposed at both ends of the arc-shaped body 1511. Both connecting components extend toward the internal space of the arc-shaped body 1511 and are used to connect the symmetrical connection points on both sides of the aero-engine.

[0136] In this embodiment, the two main connection components 152 constitute the main load-bearing points of the engine and are used to dock with the standard interfaces on the main unit body of the engine, such as the fan unit.

[0137] Understandably, two main connecting components 152 are used to connect the symmetrical connection points on both sides of the engine, forming a dual-point main support structure. Compared with single-point suspension, dual-point support can better resist the torsional moment of the workpiece itself, and can more stably control the workpiece posture during rolling operations, preventing unnecessary swaying.

[0138] In one embodiment, the main connecting assembly 152 includes a main load-bearing pin base 1521, a main load-bearing pin fixing seat 1522, and a main load-bearing pin 1523. The main load-bearing pin base 1521 is fixedly connected to the arc-shaped body 1511, the main load-bearing pin fixing seat 1522 is connected to the main load-bearing pin base 1521, and the main load-bearing pin 1523 is detachably connected to the main load-bearing pin fixing seat 1522.

[0139] In this embodiment, the main load-bearing pin base 1521 is a base connecting the arc-shaped body 1511 and the entire main connecting assembly 152. The main load-bearing pin base 1521 is connected to the end of the arc-shaped body 1511 and extends along the first direction X. The main load-bearing pin fixing seat 1522 is embedded in the limiting groove of the main load-bearing pin base 1521. The main load-bearing pin 1523 is a pin component that directly mates with the engine interface. It is connected to the main load-bearing pin base 1521 through the main load-bearing pin fixing seat 1522. The main load-bearing pin 1523 extends generally toward the interior of the arc-shaped body 1511, so that its end can be connected to the aircraft engine.

[0140] Understandably, the main load-bearing pin 1523, as a vulnerable or adaptable component that comes into direct contact with the engine, is easily detachable to facilitate quick replacement according to different engine interfaces or repair after damage, thus improving the versatility and maintainability of the lifting equipment.

[0141] In one embodiment, the main load-bearing pin fixing seat 1522 includes a fixing part 15221 and a detachable part 15222. The fixing part 15221 is fixedly connected to the main load-bearing pin base 1521, and the detachable part 15222 is detachably connected to the fixing part 15221 by a plurality of locking nuts 1524. The main load-bearing pin 1523 is clamped between the fixing part 15221 and the detachable part 15222.

[0142] Understandably, the main load-bearing pin holder 1522 is designed as an openable structure consisting of a fixing part 15221 and a detachable part 15222. The detachable part 15222 can be opened by removing the locking nut 1524, allowing for easy insertion and removal of the clamped main load-bearing pin 1523. This design simplifies the replacement of the load-bearing pin and improves on-site operational efficiency compared to methods requiring complete disassembly of the holder.

[0143] In one embodiment, the main connecting assembly 152 further includes a plurality of anti-fall pins 1525, the axis of which is parallel to the axis of the main load-bearing pin 1523. The fixing part 15221 is fixedly connected to the main load-bearing pin base 1521 via the anti-fall pins 1525, and the detachable part 15222 is also detachably connected to the main load-bearing pin base 1521 via the anti-fall pins 1525.

[0144] In this embodiment, the anti-fall pin 1525 is a locking pin that passes through the corresponding hole on the detachable part 15222 and the main load-bearing pin base 1521, or the corresponding hole on the fixing part 15221 and the main load-bearing pin base 1521. Even if all the locking nuts 1524 fail, the presence of the anti-fall pin 1525 can prevent the detachable part 15222 from opening accidentally, providing an extra layer of structural redundancy protection for the main load-bearing pin 1523.

[0145] Understandably, this embodiment adds a fall arrestor pin 1525 as a second layer of connection protection on top of the locking nut 1524 connection. The fall arrestor pin 1525 connects the detachable part 15222 to the fixed part 15221 via a pin connection. Its function is that even if all the locking nuts 1524 become loose or fail, the fall arrestor pin 1525 can still maintain the connection between the detachable part 15222 and the fixed part 15221, thereby preventing the main load-bearing pin 1523 from falling off, and improving the structural reliability of the main connection interface.

[0146] In one embodiment, the main connection assembly 152 further includes a multi-dimensional force sensor 1526, which is sandwiched between the top wall of the main load-bearing pin base 1521 and the fixing part 15221, and is located on the side of the fixing part 15221 away from the main load-bearing pin 1523 along the second direction Z.

[0147] In this embodiment, the multi-dimensional force sensor 1526 is a six-dimensional force sensor capable of simultaneously measuring forces in the X, Y, and Z directions and torques about these three axes. Its X-axis load measurement range is no less than 5000 N, and its Z-axis load measurement range is no less than 30000 N. The measurement data can be wirelessly uploaded to a host computer in real time and displayed on the hoisting equipment's built-in display screen.

[0148] Understandably, the multi-dimensional force sensor 1526 is integrated into the main load-bearing path, enabling real-time measurement of forces in multiple directions at the connection point. During precision mating, the sensor data can be fed back to the control system or operator to determine the contact state and the magnitude of the contact force. This facilitates flexible contact and force-controlled assembly, reducing the risk of damage to precision mating surfaces due to excessive impact forces.

[0149] Further integration Figures 18 to 19 As shown, in one embodiment, the hoisting equipment is also used to detachably connect with a rear ring follower tool 16, which is spaced apart from the active rotation component 151 along a first direction X. The rear ring follower tool 16 is used to detachably connect with the end of the aero-engine to cooperate with the active rotation component 151 to maintain the stability of the aero-engine rotating about its axis.

[0150] In this embodiment, the rear ring follower tool 16 is used for auxiliary hanging during product roll installation, especially suitable for long engine units or other unit bodies, to prevent sagging or vibration during roll.

[0151] Understandably, the introduction of the rear ring follower fixture 16 adds an extra support point to the hoisted aero-engine. For long engines or units, the original two-point support may cause deflection or vibration during roll due to insufficient rigidity of the workpiece itself. The additional support provided by the rear ring follower fixture 16 can effectively suppress such deformation and vibration, thereby maintaining the stability of long workpieces during roll.

[0152] In one embodiment, the rear ring follower tooling 16 includes a connecting frame 161 and a C-shaped frame 162. The connecting frame 161 is detachably connected to the hanger 133 of the second support mechanism 13, and the connecting frame 161 is slidably connected to the C-shaped frame 162. The C-shaped frame 162 is used for detachable connection to the end of the aero-engine.

[0153] In this embodiment, the connecting frame 161 and the C-frame 162 are slidably connected by an arc-shaped slide rail. The radius of curvature and center of the arc-shaped slide rail match the rotation center of the rotating mechanism 15, ensuring that the C-frame 162 can move synchronously and without interference when the engine is rolling.

[0154] Understandably, when the main support point drives the engine to roll, the connection point at the engine end is also in circular motion. The C-frame 162 needs to slide relative to the relatively fixed connecting frame 161 to accommodate this movement. This allows the auxiliary support point to rotate with the main support point, achieving coordinated movement between the main and auxiliary support points and avoiding harmful additional stress on the engine due to mismatched movements.

[0155] In one embodiment, the end of the connecting frame 161 is provided with a connecting pin 1611 protruding along the first direction X, and the hanger 133 is provided with a connecting groove recessed along the second direction Z. The connecting pin 1611 is configured to be inserted into the connecting groove from top to bottom along the second direction Z. The hanger 133 is provided with a first tooling sensor 164 for detecting whether the connecting frame 161 is connected to the hanger 133.

[0156] In this embodiment, this mounting method utilizes the tooling's own weight to achieve self-locking, making installation and disassembly very convenient. The first tooling sensor 164 can be a proximity switch or a photoelectric sensor, used to send a confirmation signal to the control system that the tooling is in place.

[0157] Understandably, the engagement of the connecting pin 1611 with the connecting slot allows for quick installation through a lifting and insertion method, facilitating the rapid attachment and detachment of the rear ring follower tooling 16. Simultaneously, the significant weight of the aircraft engine ensures a secure attachment. The first tooling sensor 164 is used to electrically confirm whether the connecting frame 161 is correctly installed on the hanger 133. The control system can utilize the sensor's signal for logical interlocking, allowing the next operation only after confirming the tooling is properly installed.

[0158] In one embodiment, the two ends of the connecting frame 161 are detachably connected to the hanger 133, and the middle section of the connecting frame 161 is slidably connected to the C-frame 162 via an arc-shaped guide rail. The rear ring follower tooling 16 also includes a sensing pin 163, which is detachably connected to both the connecting frame 161 and the C-frame 162 to keep the rear ring follower tooling 16 in a locked state. The sensing pin 163 is connected to the unlock detection position of the connecting frame 161 and can be sensed by a second tooling sensor 165, generating a signal that the roll restriction is released.

[0159] In this embodiment, the sensing pin 163 is inserted into the locking position (position 1) when not in operation, fixing the C-frame 162 and the connecting frame 161 together to prevent shaking during transportation and hoisting. When preparing for the rolling operation, the sensing pin 163 must be pulled out and inserted into another designated position (position 2), which corresponds to the setting of the second tooling sensor 165. Only when the second tooling sensor 165 detects that the pin is in place will the control system release the lock on the rotating mechanism 15 and issue an audible and visual alarm to indicate that the pin has been pulled out.

[0160] Understandably, the sensing pin 163 serves a dual purpose: during transport or when not in operation, it locks the C-frame 162 and connecting frame 161 to prevent them from wobbling; during preparation, the operator must pull out the pin to unlock it and insert it into the unlock detection position. The second tooling sensor 165 can only sense the pin at this unlock detection position. The control system is configured to allow the main unit's roll function to start upon receiving a roll restriction release signal from the sensor. This process binds the physical operation (pulling out the pin) with the electrical signal (sensor sensing), ensuring that the operator must complete the unlocking action before rolling, thus avoiding damage to the lifting equipment or workpiece caused by forced rolling due to forgetting to unlock.

[0161] It should be explained that, for ease of understanding, the diagram shows that both the locking position (position 1) and another designated position (position 2) are equipped with sensor pins 163. During normal use, one sensor pin 163 is in either position 1 or position 2. Position 1 is approximately located at the rotation axis between the C-shaped frame 162 and the connecting frame 161, and position 2 is approximately located near the connection between the connecting frame 161 and the hanger 133.

[0162] In other embodiments, the hoisting equipment may also integrate lighting strips to ensure sufficient illumination in the operating space below the equipment, with an illuminance of no less than 860 lux in the work area. Additionally, an LED display screen can be configured to display key information such as travel speed, roll angle, total load, and Z-axis load on the left and right main supports in real time. For convenient ground positioning, a linear laser can also be installed above the hoisting equipment to project its central axis onto the ground.

[0163] It is understood that although the hoisting equipment of this application is applied to aero engines, those skilled in the art will understand that it is also applicable to the hoisting and assembly of other large precision cylindrical workpieces (such as gas turbines, precision shafts, etc.) that have high requirements for safety and precision.

[0164] The embodiments described herein are preferred embodiments and are not intended to limit the scope of protection of this application. Identical components are represented by the same reference numerals. All equivalent changes made to the structure, shape, and principle of this application should be included within the scope of protection of this application.

Claims

1. A hoisting device applied to a pulsed production line for aero-engines, characterized in that, The hoisting equipment is used at least to drive the aero-engine to move linearly along a first direction (X) and a second direction (Z) and to drive the aero-engine to rotate around its own axis. The hoisting equipment includes: The first support mechanism (11) includes a support frame (111) and a crash protection bracket (112), wherein the crash protection bracket (112) is connected to both ends of the support frame (111) along the first direction (X); The walking mechanism (12) includes an active walking component (121) and a driven walking component (122). Both the active walking component (121) and the driven walking component (122) are fixedly connected to the support frame (111) and are configured to slide in connection with the guide rail of the aero-engine pulse production line to drive the first support mechanism (11) to move along the first direction (X). The second support mechanism (13) includes a lifting frame (131) and an arc frame (132). The lifting frame (131) is slidably connected to the support frame (111) and their projection portions overlap along the second direction (Z). The arc frame (132) is fixedly connected to the lifting frame (131). The lifting mechanism (14) includes a lifting guide assembly (141) and a lifting drive assembly (142). The lifting frame (131) and the support frame (111) are slidably connected along the second direction (Z) through the lifting guide assembly (141). The driving part of the lifting drive assembly (142) is connected to the support frame (111) and its driven part is connected to the lifting frame (131). It is used to drive the lifting frame (131) to move the arc frame (132) relative to the first support mechanism (11) along the second direction (Z). The lifting drive assembly (142) has multi-stage physical braking. The rotating mechanism (15) includes an active rotating component (151) and a main connecting component (152). The main connecting component (152) is fixedly connected to the end of the active rotating component (151) and is used to connect the aircraft engine. The active rotating component (151) is connected to the arc frame (132) and is used to drive the aircraft engine to rotate around its own axis.

2. The hoisting equipment applied to the pulse production line of aero-engines according to claim 1, characterized in that: The support frame (111) includes a first crossbar component (1111) and two support components (1112). The two support components (1112) are spaced apart along a third direction (Y) perpendicular to the first direction (X). The first crossbar components (1111) are connected to the two support components (1112) at their respective ends spaced apart along the third direction (Y). There are multiple anti-collision brackets (112). Each support component (1112) is connected to an anti-collision bracket (112) at its respective ends spaced apart along the first direction (X). The anti-collision brackets (112) extend along the first direction (X).

3. The hoisting equipment applied to the pulse production line of aero-engines according to claim 1, characterized in that: The lifting frame (131) includes an upper frame (1311), a side frame (1312), and a lower frame (1313). The upper frame (1311) and the lower frame (1313) are respectively connected to the two opposite sides of the side frame (1312) along the second direction (Z). The upper frame (1311) is located above the support frame (111) along the second direction (Z). The side frame (1312) is slidably connected to the support frame (111) through the lifting guide assembly (141). The arc-shaped frame (132) is fixedly connected to the lower frame (1313) and is located on the side of the lower frame (1313) away from the support frame (111) along the second direction (Z).

4. The hoisting equipment applied to the pulse production line of aero-engines according to claim 3, characterized in that: The second support mechanism (13) further includes at least two sets of hangers (133) and multiple hook assemblies (134); the two sets of hangers (133) are located on both sides of the lower frame (1313) along the first direction (X) and are respectively connected to the lower frame (1313), the hangers (133) extending along the first direction (X); each hook assembly (134) includes a hook sliding component (1341) and a hook body (1342), each of the... A hook sliding component (1341) is connected to one of the aforementioned hangers (133), and each hook body (1342) is slidably connected to one of the aforementioned hangers (133) via a hook sliding component (1341) for adjusting the position of the hook body (1342) relative to the hanger (133) along the first direction (X). The lower part of the hook body (1342) along the second direction (Z) is provided with a hook portion (13421) for connecting an aircraft engine.

5. The hoisting equipment applied to the pulse production line of aero-engines according to claim 1, characterized in that: The lifting mechanism (14) further includes a lifting position detection component (143), which includes a position detection sensor (1431) and a trigger (1432). The position detection sensor (1431) is fixedly connected to the support frame (111), and the trigger (1432) is fixedly connected to the lifting frame (131) and can move along the second direction (Z) with the lifting frame (131). The trigger (1432) is slidably disposed relative to the position detection sensor (1431) along the second direction (Z). The lifting mechanism (14) is used to trigger the positioning detection sensor (1431) to generate a positioning signal when the lifting frame (131) moves to the lifting limit position; the lifting mechanism (14) also includes a lifting parking pin (144), which is fixedly connected to the support frame (111); the lifting frame (131) includes a plurality of inserts (1314) spaced along the second direction (Z), which are used for the lifting parking pin (144) to be inserted therein to lock the lifting frame (131) and the support frame (111).

6. The hoisting equipment applied to the pulse production line of aero-engines according to claim 1, characterized in that: The lifting drive assembly (142) includes a lifting drive component (1421), a shaft-end brake (1422), and a linear brake component (1423). Both the lifting drive component (1421) and the linear brake component (1423) extend along the second direction (Z). The driving part of the lifting drive component (1421) is connected to the support frame (111), and its driven part is connected to the lifting frame (131). The driving part of the lifting drive component (1421) is... The drive motor is equipped with a braking mechanism. The driven part of the lifting drive component (1421) is a lead screw. The shaft end brake (1422) is connected to the driving part of the lifting drive component (1421) and is used to brake the driven part of the lifting drive component (1421). The linear brake component (1423) is connected to the support frame (111) and the lifting frame (131) respectively and is used to brake the support frame (111) and the lifting frame (131).

7. The hoisting equipment applied to the pulse production line of aero-engines according to claim 1, characterized in that: The arc-shaped frame (132) has a rotation guide groove (1321), which is recessed towards the lifting frame (131) along the second direction (Z) and is arc-shaped. The active rotation component (151) includes a rotation transmission component (1510) and a rotation drive component (1513). The rotation transmission component (1510) is slidably disposed in the rotation guide groove (1321), and the rotation drive component (1513) is disposed on the arc-shaped frame (132). The rotation drive component (1513) is drivenly connected to the rotation transmission component (1510) and is used to drive the rotation transmission component (1510) to rotate in a circular motion.

8. The hoisting equipment applied to the pulse production line of aero-engines according to claim 7, characterized in that: The rotary transmission component (1510) includes an integrally connected arc-shaped body (1511) and a transmission gear ring (1512). The arc-shaped body (1511) has an annular cross-section. The transmission gear ring (1512) is connected to the arc-shaped body (1511) and protrudes from the upper wall of the arc-shaped body (1511) along the second direction (Z). The transmission gear ring (1512) extends in an arc shape. The end of the arc-shaped body (1511) is connected to the main connecting assembly (1512). 52), the transmission gear ring (1512) and the rotary drive component (1513) are driven to be engaged; the rotary drive component (1513) includes a rotary drive component (15131) and a rotary output component (15132) that are driven to be connected. The rotary drive component (15131) is fixedly disposed with the arc frame (132), and the rotary output component (15132) is disposed in the rotation guide groove (1321) and driven to be connected with the transmission gear ring (1512).

9. The hoisting equipment applied to the pulse production line of aero-engines according to claim 8, characterized in that: The transmission gear ring (1512) has multiple spaced arc-shaped tooth grooves (15121) on the same side away from the arc-shaped body (1511), and adjacent arc-shaped tooth grooves (15121) are separated by tooth columns (15122); the rotary output component (15132) includes a fixed plate (15133) and multiple meshing cylinders (15134), the fixed plate (15133) is connected to the driving end of the rotary drive component (15131) and is configured to be driven to rotate, and the multiple meshing cylinders (15134) are evenly spaced around the rotation axis of the rotary output component (15132); a single arc-shaped tooth groove (15121) The drive gear ring (1512) is used to accommodate one of the engagement cylinders (15134) so ​​that the drive gear ring (1512) engages with the rotary drive member (15131); the drive rotation assembly (151) also includes a rotary parking pin (1514), which is fixedly connected to the arc frame (132), and the rotary parking pin (1514) has a cylindrical pin head (15141); the cylindrical pin head (15141) is configured to be driven to extend or retract in the first direction (X) within the rotation guide groove (1321) for extending into the arc tooth groove (15121) to lock the rotary transmission member (1510).

10. The hoisting equipment applied to the pulse production line of aero-engines according to claim 8, characterized in that: The main connecting assembly (152) includes a main load-bearing pin base (1521), a main load-bearing pin fixing seat (1522), and a main load-bearing pin (1523). The main load-bearing pin base (1521) is fixedly connected to the arc-shaped body (1511), the main load-bearing pin fixing seat (1522) is connected to the main load-bearing pin base (1521), and the main load-bearing pin (1523) is detachably connected to the main load-bearing pin fixing seat (1522). The main load-bearing pin fixing seat (1522) includes a fixing part (15221) and a detachable part (15222). The fixing part (15221) is fixedly connected to the main load-bearing pin base (1521), and the detachable part (15222) is detachable. The main connecting assembly (152) is detachably connected to the fixed part (15221) via several locking nuts (1524). The main bearing pin (1523) is sandwiched between the fixed part (15221) and the detachable part (15222). The main connecting assembly (152) also includes a plurality of anti-fall pins (1525). The axis of the anti-fall pin (1525) is parallel to the axis of the main bearing pin (1523). The fixed part (15221) is fixedly connected to the main bearing pin base (1521) via the anti-fall pin (1525). The detachable part (15222) is also detachably connected to the main bearing pin base (1521) via the anti-fall pin (1525).

11. The hoisting equipment applied to the pulse production line of aero-engines according to claim 1, characterized in that: The hoisting equipment is also used to detachably connect with a rear ring follower fixture (16), which is spaced apart from the active rotating assembly (151) along the first direction (X); the rear ring follower fixture (16) includes a connecting frame (161) and a C-frame (162), the connecting frame (161) is detachably connected to the second support mechanism (13), the connecting frame (161) is slidably connected to the C-frame (162), and the C-frame (162) is used to detachably connect to the end of the aero-engine; the rear ring follower fixture (16) It also includes a sensing pin (163) which is detachably connected to both the connecting frame (161) and the C-frame (162) to lock the rear ring follower tooling (16); the sensing pin (163) is also used to connect to the unlock detection position of the connecting frame (161) when it is separated from the C-frame (162), and can be sensed by a second tooling sensor (165) configured to issue a roll limit release signal when the sensing pin (163) is sensed.

Images