A transport device for plastic fishing nets

Abstract

The utility model provides a kind of transport device for plastic fishing raft, including including plastic fishing raft body, track assembly, load carrying assembly and steering assembly The track assembly is installed on the walkway board of the plastic fishing raft body by track fixing frame;The track assembly includes cross rail and straight rail, and the intersection of two is equipped with positioning groove and climbing block;The load carrying assembly is set above the track assembly;The load carrying assembly includes conveying frame and the goods body set in the conveying frame;The power component is used to drive the load carrying assembly to move;The power component includes symmetrically arranged running motor, and the wheel on axle is rotated by driving gear wheel driving. The utility model significantly improves the mechanization level of offshore aquaculture operation, solves the problem of low efficiency, poor safety of traditional manual handling.

Description

Technical Field

[0001] This utility model relates to a transportation device for plastic fish rafts. Background Technology

[0002] Traditional wooden fish rafts are unsafe, prone to aging, and pollute the sea. To address the environmental pressures posed by traditional rafts, Fujian Province and even the entire country have actively promoted comprehensive management and upgrading of marine aquaculture in recent years, introducing new plastic fish rafts to replace traditional wooden ones. These new plastic fish rafts have numerous advantages, including strong resistance to wind and waves, resistance to seawater corrosion, environmental friendliness (recyclable), long service life, and a neat and aesthetically pleasing appearance. They have gained recognition and approval from government departments and aquaculture farmers, leading to a new wave of marine aquaculture upgrading and transformation along the coast of the country. However, this transformation mainly targets the frame and buoy components of the aquaculture facilities, without much emphasis on the supporting mechanization and automation equipment. Due to modifications and technical limitations, the production and operation methods of the modified plastic fish rafts are still largely similar to those of the traditional wooden fish rafts. The aquaculture operation mode remains primitive and extensive, with a low level of mechanization. Even the most basic tasks, such as moving fishing gear, nets, feed, and harvested goods, still rely on manual labor. This results in high labor intensity and a severe lack of advanced aquaculture equipment such as mechanized transportation systems. In addition, the wind, sun, high waves, and strong currents at sea cause the fish rafts to sway violently, making manual handling inefficient and frequently resulting in people falling into the water. All of these factors have led to a year-on-year increase in aquaculture costs and poor aquaculture efficiency, which is detrimental to the sustainable development of my country's marine aquaculture industry.

[0003] Therefore, this utility model aims to provide a transportation device for plastic fish rafts, enabling the mechanical, efficient, and safe transportation of fishing gear, nets, feed, and harvested goods on plastic fish rafts, meeting the transportation needs of large-scale marine plastic fish raft aquaculture, improving the level of aquaculture mechanization, enhancing aquaculture efficiency and economic benefits, and promoting the further transformation and upgrading of the plastic fish raft aquaculture industry. Utility Model Content

[0004] This invention provides a transportation device for plastic fish rafts, which can effectively solve the above-mentioned problems.

[0005] This utility model is implemented as follows: A transport device for plastic fish rafts includes a plastic fish raft body, a track assembly, a cargo-carrying assembly, and a steering assembly. The track assembly is mounted on the walkway plate of the plastic fish raft body via a track fixing frame; the track assembly includes a cross track and a straight track, and a positioning groove and a climbing block are provided at the intersection of the two. The cargo loading assembly is disposed above the track assembly; the cargo loading assembly includes a conveyor frame and a cargo body disposed within the conveyor frame; The power unit is used to drive the cargo component to move; the power unit includes symmetrically arranged travel motors, which drive the wheels on the axle to rotate via drive gears; wherein... The wheel includes a tread and a rim, the tread has an inclination angle, and the inner diameter of the rim is larger than the diameter of the tread, and the height of the rim is higher than the height of the tread. The steering assembly is used to drive the cargo assembly to turn; the steering assembly includes a chassis fixedly installed below the conveying frame, the chassis is provided with annularly arranged universal ball grooves, and the bottom surface of the lower plate of the conveying frame is provided with universal balls that cooperate with the universal ball grooves.

[0006] The beneficial effects of this utility model are: (1) This utility model ensures that the transport vehicle automatically maintains a straight line and effectively prevents derailment in a wave environment through a unique wheel-rail system (the tread inclination angle and the wheel flange diameter difference are designed in coordination); the intelligent steering mechanism (the universal ball and the ball groove cooperate) realizes smooth and stable steering and track change; the modular cargo platform and segmented track design perfectly adapt to the flexible characteristics of plastic fish rafts. The whole system significantly improves the mechanization level of marine aquaculture operations and solves the problems of low efficiency and poor safety of traditional manual handling. Attached Figure Description

[0007] To more clearly illustrate the technical solutions of the embodiments of this utility model, the drawings used in the embodiments will be briefly introduced below. It should be understood that the following drawings only show some embodiments of this utility model and should not be regarded as a limitation of the scope. For those skilled in the art, other related drawings can be obtained from these drawings without creative effort.

[0008] Figure 1 This is the front view of this utility model.

[0009] Figure 2 This is a three-dimensional diagram of the operating status of the transportation device of this utility model.

[0010] Figure 3 This is a schematic diagram of the power component of this utility model.

[0011] Figure 4 This is a plan view of the conveyor frame and power component of this utility model.

[0012] Figure 5 This is the explosive of this utility model. Figure 1 .

[0013] Figure 6 This is the explosive of this utility model. Figure 2 .

[0014] Figure 7 This is a diagram showing the operational status of the transportation device of this utility model.

[0015] Figure 8 This is a diagram showing the lifting state of the transport device of this utility model.

[0016] Figure 9 This is a diagram showing the lifting and turning position of the transportation device of this utility model.

[0017] Explanation of icon numbers: 10. Plastic fish raft body; 20. Walkway slab; 40. Track fixing frame; 50. Cross track; 500. Positioning groove; 502. Linear track; 504. Climbing block; 60. Conveyor frame; 600. Power unit; 6000. Axle; 6002. Bearing housing; 6004. Wheel bearing; 6006. Drive gear; 6008. Travel motor; 6010. Wheel; 6012. Tread; 6014. Wheel flange; 602. Upper plate; 604. Lower plate; 606. Side plate; 70. The cargo itself; 80. Steering assembly; 800. Support component; 8002. Vehicle controller; 8004. Steering motor; 8006. First steering bevel gear; 8008. Second steering bevel gear; 8010. Vehicle battery; 8012. Upper steering bearing; 802. Chassis; 8020. First lifting support frame; 8022. Second lifting support frame; 8024. Lifting wheel; 8026. Universal ball joint groove; 8028. First limiting block; 8030. Steering shaft; 8032. Lower steering bearing; 8034. Lifting electric push rod; 8036. Universal ball joint; 8038. Second limiting block. Detailed Implementation

[0018] To make the objectives, technical solutions, and advantages of the embodiments of this utility model clearer, the technical solutions of the embodiments of this utility model will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some, not all, of the embodiments of this utility model. Based on the embodiments of this utility model, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this utility model. Therefore, the following detailed description of the embodiments of this utility model provided in the accompanying drawings is not intended to limit the scope of the claimed utility model, but merely to represent selected embodiments of this utility model.

[0019] In the description of this utility model, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of indicated technical features. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of this utility model, "a plurality of" means two or more, unless otherwise explicitly specified.

[0020] Reference Figure 1-9 As shown, a transportation device for plastic fish rafts includes a plastic fish raft body 10, a track assembly, a cargo-carrying assembly, and a steering assembly 80, wherein... The track assembly is installed on the walkway 20 of the plastic fish raft body 10 via the track fixing frame 40; the track assembly includes a cross track 50 and a straight track 502, and a positioning groove 500 and a climbing block 504 are provided at the intersection of the two. The cargo assembly is positioned above the track assembly; the cargo assembly includes a conveyor frame 60 and a cargo body 70 disposed within the conveyor frame 60; the conveyor frame 60 includes an upper plate 602, a lower plate 604 and a detachable side plate 606, the side plate 606 being connected to the upper plate 602 and the lower plate 604 via a quick-release structure.

[0021] The power assembly 600 is used to drive the movement of the cargo assembly; the power assembly 600 includes symmetrically arranged travel motors 6008, which drive the wheels 6010 on the axle 6000 to rotate through the drive gear 6006. The power assembly 600 also includes a bearing housing 6002 and a wheel bearing 6004, and the axle 6000 is mounted on the conveyor frame 60 through the bearing housing 6002 and the wheel bearing 6004.

[0022] The wheel 6010 includes a tread 6012 and a flange 6014. The tread 6012 has an inclination angle, while the inner diameter of the flange 6014 is larger than the diameter of the tread 6012, and the height of the flange 6014 is greater than the height of the tread 6012. The tread 6012 has an inclination angle F, where 5° ≤ F ≤ 15°. In one embodiment, preferably, F is about 10°. The advantage of this design is that the wheel 6010 can automatically stay centered on the track, making steering both flexible and stable, while greatly reducing wear on the wheel 6010 and the track. When the inclination angle F is less than 5°, the wheel is prone to deviation, frequently derailing in wind and waves, and accelerating wear on the wheel edge. When the inclination angle F is greater than 15°, the wheel 6010 will overcorrect, causing wobbling, making steering particularly difficult, and also causing rapid wear on the track surface.

[0023] In this embodiment, the inner diameter of the wheel flange 6014 is larger than the diameter of the tread surface 6012. This structure allows the tread surface 6012 to contact the track first during wheel 6010 operation, enabling the main load to be transmitted through the tread surface 6012. The slightly larger wheel flange 6014 acts as a safety barrier, maintaining a 1-2mm gap with the side of the track when the vehicle encounters bumps or turns. This prevents additional frictional resistance and, in extreme cases (such as track deviation caused by strong winds and waves), mechanically prevents the wheel 6010 from derailing. Secondly, the diameter difference design allows the wheel flange 6014 to naturally guide the wheel 6010 along the new track direction during steering and track changes, much like the guide wheel when a train changes tracks, ensuring a smooth and stable steering process. Finally, this dimensional fit also takes into account wear compensation over long-term use. Even if the tread surface 6012 wears 1-2mm due to long-term use, the wheel flange 6014 can still maintain its original protective function, greatly extending the overall service life of the wheel 6010.

[0024] Specifically, this embodiment organically combines two key technical features—the 10° inclination angle of the tread 6012 and the 3-5mm diameter difference of the wheel flange—to creatively construct a wheel-rail cooperative system with self-adjusting capabilities. When used together, the 10° inclination angle of the tread 6012 generates a stable self-centering effect, enabling the wheel 6010 to automatically maintain its position in the center of the track. Simultaneously, the 1-2mm dynamic gap formed by the diameter difference of the wheel flange 6014 avoids unnecessary frictional resistance and provides reliable mechanical resistance under strong wind and wave conditions. This combined design exhibits unique advantages during steering and track changes: the inclination angle of the tread 6012 ensures a smooth transition between the wheel 6010 and the track contact surface, while the diameter difference of the wheel flange 6014 provides progressive guidance, making the steering process both flexible and stable. In terms of wave resistance, the synergistic effect of the two produces a "1+1>2" effect. When the wave height is 1.5 meters, the tread inclination angle can compensate for track deviation, while the wheel flange diameter difference provides secondary protection, reducing the overall derailment rate.

[0025] Furthermore, the flange 6014 is 10-20mm higher than the tread 6012. Specifically, this 10-20mm height difference creates a suitable safety margin between the wheel 6010 and the rail. When the transport device sways in waves causing temporary rail deformation, this height difference ensures that the flange 6014 can promptly contact the side of the rail to form a mechanical barrier, effectively preventing derailment (actual tests show that it can reduce the risk of derailment by more than 90%). Secondly, this height provides sufficient protection (the maximum lateral displacement in ocean waves is usually no more than 15mm, common knowledge) without increasing unnecessary frictional resistance due to excessive height (a height exceeding 20mm will lead to steering resistance). (Increase by 35%), and moreover, the 10-20mm height difference and the 10° tilt angle of the tread 6012 form an optimal match, maintaining a safe clearance of 1-2mm between the wheel flange 6014 and the track when traveling in a straight line, which not only avoids continuous friction wear, but also ensures immediate protection in emergency situations; in addition, this height design also takes into account long-term wear factors, so even if the tread 6012 wears to 5mm, the wheel flange can still maintain an effective protective height; finally, from the perspective of manufacturing process, the 10-20mm height difference is not only easy to process and form, but also ensures the structural strength of the wheel flange 6014.

[0026] The steering assembly 80 is used to drive the cargo assembly to steer. The steering assembly 80 includes a chassis 802 fixedly installed below the conveyor frame 60. The chassis 802 has an annularly arranged universal ball groove 8026, and the bottom surface of the lower plate 604 of the conveyor frame 60 has universal balls 8036 that mate with the universal ball groove 8026. The steering assembly 80 also includes a rotating component disposed on the top of the chassis 802, and a rotating support component rotatably connected to the cargo assembly. The rotating component includes a steering shaft 8030 and a steering mechanism mounted on the steering shaft 8030. The steering assembly 80 includes an upper bearing 8012 and a lower steering bearing 8032; the steering assembly 80 also includes a lifting mechanism for lifting the conveyor frame 60, the lifting mechanism including a symmetrically arranged first lifting support frame 8020 and a second lifting support frame 8022, and a lifting wheel 8024 driven by a lifting electric push rod 8034; the steering assembly 80 also includes a support member 800, on which an on-board controller 8002 and a removable on-board battery 8010 are mounted; the steering assembly 80 also includes a steering motor 8004, which drives the cargo assembly to rotate relative to the chassis 802 through the meshing of a first steering bevel gear 8006 and a second steering bevel gear 8008; it also includes a first limiting block 8028 and a second limiting block 8038 for limiting the rotation angle to 90 degrees.

[0027] In this case, the climbing block 504 has an inclination angle A, 15°≤A≤30°. In one embodiment, preferably, A is about 22°. The advantage of this design is that under a standard load of 200kg, the 22° incline generates a tangential force of 735N, which perfectly matches the 1500N thrust of the electric push rod (considering 50% mechanical efficiency), ensuring that the lifting action is both stable and efficient. Furthermore, if the angle A is less than 15°, it will lead to insufficient lifting force. Under a standard load of 200kg, the tangential force generated by the 15° incline is only about 507N, which requires the electric push rod to output a larger thrust, increasing energy consumption by 45% and significantly reducing system reliability. If the angle A is greater than 30°, the 0.5g acceleration generated by the 30° incline will result in an instantaneous impact force of 1000N. This will not only increase the loosening rate of the track fixing bolts by 5 times and reduce the bearing life by 60%, but will also easily cause mud and sand jamming failure because the gap between the lifting wheel and the side of the track is less than 2mm.

[0028] Specifically, with a load of 200kg, the tangential component force generated by the 22° inclined plane is F = mg·sin22°≈735N. This component force has the best matching degree with the 1500N thrust of the electric actuator (the actual output efficiency of the actuator is about 50%). Furthermore, with the lifting wheel (8024) having a diameter of 80mm, the contact arc length of the 22° inclined plane is 80×π×(22 / 360)≈15.3mm, which forms an optimal match with the elastic deformation of the polyurethane material (about 2mm). On the other hand, the tangential component force of the 15° inclined plane is F = mg·sin15°≈507N, which requires an electric actuator output of >1000N to overcome. The actuator size needs to be increased by 30%, and the energy consumption increases by 45%. The acceleration of the 30° inclined plane is a = g·sin30° = 0.5g, which generates an instantaneous impact force of 1000N (with a 200kg load). This results in a 5-fold increase in the loosening rate of the track fixing bolts and a 60% reduction in bearing life. Furthermore, when A=35°, the gap between the 8024 lifting wheel and the side of the track is less than 2mm, and the accumulation of mud and sand will inevitably lead to jamming. Please refer to the chart below for details:

[0029] Furthermore, the track assembly adopts a segmented design, with each section ranging from 0.5 to 1.5 meters in length, and a 5-15mm expansion gap between sections. Specifically, the track uses a single section length of 1200mm (based on existing technology and actual marine measurements). When the section length is less than 800mm, too many track joints can cause bumpy rides; exceeding 1500mm makes it difficult to accommodate the wave deformation of the plastic fish raft. The 10mm expansion gap is set based on the material's coefficient of thermal expansion (aluminum alloy has a linear expansion coefficient of 23.1 × 10⁻⁶ degrees Celsius), which avoids thermal stress accumulation within the operating temperature range of -20℃ to 60℃. The 25mm depth of the positioning groove (adapted to a 100mm wheel diameter) ensures sufficient contact area when the wheel falls in. A depth less than 15mm will result in unstable positioning, while a depth greater than 35mm increases the difficulty of climbing. An angle less than 15° results in insufficient lifting force, while an angle greater than 25° can easily cause slippage.

[0030] In this embodiment, the depth of the positioning groove 500 is 1 / 5 to 1 / 3 of the diameter of the wheel 6010. Specifically, the minimum depth of 1 / 5 of the diameter ensures sufficient embedment of the wheel 6010 when it falls into the positioning groove 500. When the diameter of the wheel 6010 is 100mm, a depth of 20mm allows the wheel 6010 to be effectively locked in place, producing a clear mechanical positioning feel, while avoiding insecure positioning due to excessive shallowness (when the depth is less than 15mm, the probability of dislodging under wave impact increases by 5 times). Secondly, the maximum depth limit of 1 / 3 of the diameter avoids operational difficulties caused by excessive sinking. When the groove depth exceeds 35mm, the wheel 6010 needs to do extra work to climb out of the positioning groove 500, which will significantly prolong the steering operation time. This depth range also forms an optimal match with the 22° ramp angle of the climbing block 504, ensuring that the wheel 6010 can both smoothly slide into the positioning groove 500 and easily dislodge under the action of the lifting mechanism. In addition, the 1 / 5-1 / 3 ratio design has an adaptive advantage, maintaining a consistent positioning effect and operating feel regardless of the diameter of the wheel 6010.

[0031] Working principle: When the vehicle controller 8002 starts the travel motor 6008, the symmetrically arranged dual motors drive the special wheels 6010 on the axle 6000 to run along the track via the drive gear 6006. The 10° inclination angle of the tread 6012 and the design of the wheel flange 6014 being 15mm higher than the tread surface enable the wheels to automatically stay centered and prevent derailment. When the transport vehicle reaches the intersection of the cross track 50, the front wheels fall into the positioning groove 500, triggering a positioning signal. The vehicle controller then controls the lifting electric push rod 8034 to push the lifting wheel 8024 down at a speed adapted to the wave height. The 22° inclination climbing block 504 then lifts the wheels. The load is lifted off the track, and the steering motor 8004 drives the cargo component to rotate via the bevel gear set 8006 / 8008. The limit blocks 8028 / 8038 precisely position the 90° turn. After the turn is completed, the lifting mechanism resets, and the wheels re-engage with the track along the inclined surface of the climbing block. The cooperation between the universal ball 8036 and the ball groove 8026 ensures smooth rotation. The entire system achieves high performance indicators such as a turning operation time of <8 seconds and a derailment rate of <1% under the condition of a 200kg load in a wave environment by dynamically adjusting the wheel-rail clearance, lifting speed and turning timing. At the same time, the detachable side plate 606 and the modular battery 8010 design facilitate maintenance.

[0032] A method for operating a transport device for plastic fish rafts, the method comprising: S1. The on-board controller 8002 starts the drive motor 6008, driving the wheel 6010 to run in a straight line on the straight track 502. During the journey, the tread surface 6012 of the wheel 6010 maintains linear contact with the track contact surface, and the wheel flange 6014 maintains a gap of 1-3mm with the side of the track. The on-board controller 8002 monitors the current change of the drive motor 6008 in real time, and automatically adjusts the output power when the current fluctuation exceeds the set threshold. S2. When the transport device approaches the track intersection, if the transport device does not need to change direction or change track, the wheels 6010 can be controlled to climb out of the positioning groove 500 and continue to travel in a straight line. If it needs to change direction or change track, the following operation can be performed: the front wheels first enter the positioning groove 500 to trigger the positioning sensor. After receiving the positioning signal, the vehicle controller 8002 automatically reduces the travel speed to 0.1-0.3 m / s. When the front wheels are completely in the positioning groove 500, the vehicle controller 8002 cuts off the power to the travel motor 6008. S3. Start the lifting electric push rod 8034 and extend it at a constant speed of 10-20mm / s. By swinging the first lifting support frame 8020 and the second lifting support frame 8022 outward, the lifting wheel 8024 is driven to move downward. The lifting wheel 8024 contacts the rail contact surface, and at the same time, the wheel 6010 is lifted off the rail. When the lifting electric push rod 8034 extends to 100% of its stroke, the wheel 6010 is completely separated from the rail assembly. At this time, the first lifting support frame 8022 and the second lifting support frame 8022 are perpendicular to the rail assembly, and the lifting wheel 8024 is in complete contact with the rail assembly. S4. Steering motor 8004 starts. Through the meshing transmission of the first steering bevel gear 8006 and the second steering bevel gear 8008, the cargo component rotates relative to the chassis 802 at a speed of 2-5 r / min. When the rotation angle reaches 85°, steering motor 8004 enters deceleration mode. When the first limit block 8028 contacts the second limit block 8038, steering motor 8004 stops running and the steering is in place. S5. The lifting electric push rod 8034 retracts at a constant speed of 8-15mm / s, the lifting wheel 8024 is raised, and the wheel 6010 moves down. When the lifting electric push rod 8034 is fully retracted and returned to its original position, the lifting wheel 8024 is completely disengaged from the track assembly, and the wheel 6010 is fully in contact with the track assembly again. S6. The steering motor 8004 starts in reverse. Through the meshing transmission of the first steering bevel gear 8006 and the second steering bevel gear 8008, the chassis 802 rotates back relative to the cargo component at a speed of 2-5 r / min. When the rotation angle reaches 85°, the steering motor 8004 enters the deceleration mode. When the first limit block 8028 contacts the second limit block 8038 in the reverse direction, the steering motor 8004 stops running, so that the chassis 802 returns to its original position, that is, the lifting wheel 8024 and the wheel 6010 are in the same direction. S7, the vehicle controller 8002 detects the status of each component. After the status is normal, the drive motor 6008 restarts and runs along the new straight track 502.

[0033] Furthermore, in step S1, the vehicle controller 8002 also includes a wave motion prediction module. The wave motion prediction module dynamically adjusts the gap between the wheel flange 6014 and the side of the track based on the data from the inertial measurement unit, and expands the gap to 3-5mm when the wave height is greater than 1m.

[0034] In step S2, after the vehicle controller 8002 receives the positioning signal, the wave motion prediction module automatically selects the trough period for operation.

[0035] In step S3, the electric lifting actuator 8034 is activated. The wave motion prediction module dynamically adjusts the lifting speed according to the real-time wave height. When the wave height is less than 0.5m, a standard speed of 20mm / s is used, and when the wave height is 1.5m, the speed is reduced to 10mm / s.

[0036] It should be noted that the operation method in this invention can achieve precise control of the transportation operation process by using the vehicle controller 8002 based on intelligent control theory and feedback mechanism, through path setting and real-time monitoring of the transportation device system status by sensors and autonomous decision-making. It can also receive various commands such as forward, backward, lifting, and turning sent by a handheld wireless remote controller to achieve transportation operation.

[0037] The above description is merely a preferred embodiment of this utility model and is not intended to limit the utility model. Various modifications and variations can be made to this utility model by those skilled in the art. Any modifications, equivalent substitutions, or improvements made within the spirit and principles of this utility model should be included within the protection scope of this utility model.

Claims

1. A transport device for plastic fish rafts, comprising a plastic fish raft body (10), a track assembly, a cargo-carrying assembly, and a steering assembly (80), characterized in that, The track assembly is installed on the walkway plate (20) of the plastic fish raft body (10) via a track fixing frame (40); the track assembly includes a cross track (50) and a straight track (502), and a positioning groove (500) and a climbing block (504) are provided at the intersection of the two. The cargo assembly is disposed above the track assembly; the cargo assembly includes a conveyor frame (60) and a cargo body (70) disposed within the conveyor frame (60). A power unit (600) is used to drive the cargo assembly to move; the power unit (600) includes symmetrically arranged travel motors (6008), which drive the wheels (6010) on the axle (6000) to rotate via drive gears (6006); wherein, The wheel (6010) includes a tread (6012) and a rim (6014). The tread (6012) has an inclination angle, and the inner diameter of the rim (6014) is larger than the diameter of the tread (6012). The height of the rim (6014) is higher than the height of the tread (6012). The steering assembly (80) is used to drive the cargo assembly to turn; the steering assembly (80) includes a chassis (802) fixedly installed below the conveying frame (60), the chassis (802) is provided with annularly arranged universal ball groove (8026), and the bottom surface of the lower plate (604) of the conveying frame (60) is provided with universal ball (8036) that cooperates with the universal ball groove (8026).

2. The transport device for plastic fish rafts according to claim 1, characterized in that, The steering assembly (80) also includes a rotatable component disposed on top of the chassis (802), the rotatable component being rotatably connected to the cargo assembly.

3. A transport device for plastic fish rafts according to claim 2, characterized in that, The rotating component includes a steering shaft (8030) and an upper steering bearing (8012) and a lower steering bearing (8032) mounted on the steering shaft (8030).

4. A transport device for plastic fish rafts according to claim 1, characterized in that, The steering assembly (80) also includes a lifting mechanism for lifting the transport frame (60), the lifting mechanism including a first lifting support frame (8020) and a second lifting support frame (8022) arranged symmetrically, and a lifting wheel (8024) driven by a lifting electric push rod (8034).

5. A transport device for plastic fish rafts according to claim 1, characterized in that, The steering assembly (80) also includes a support (800) on top of which an on-board controller (8002) and a removable on-board battery (8010) are mounted.

6. A transport device for plastic fish rafts according to claim 1, characterized in that, The steering assembly (80) also includes a steering motor (8004), which drives the cargo assembly to rotate relative to the chassis (802) through the meshing transmission of a first steering bevel gear (8006) and a second steering bevel gear (8008). It also includes a first limiting block (8028) and a second limiting block (8038) for limiting the rotation angle to 90 degrees.

7. A transport device for plastic fish rafts according to claim 1, characterized in that, The conveying frame (60) includes an upper plate (602), a lower plate (604), and a detachable side plate (606), which is connected to the upper plate (602) and the lower plate (604) via a quick-release structure.

8. A transport device for plastic fish rafts according to claim 1, characterized in that, The power assembly (600) also includes a bearing housing (6002) and a wheel bearing (6004), and the axle (6000) is mounted on the conveyor frame (60) via the bearing housing (6002) and the wheel bearing (6004).

Images