Double-gear synchronous driving heavy load transfer mechanism

Abstract

The utility model relates to the technical field of transfer mechanism, especially a double gear synchronous drive's heavy -duty transfer mechanism, including base subassembly, material frame subassembly and drive mechanism, and material frame subassembly is equipped with the first material frame and second material frame that are independent of each other, respectively sliding connection in base subassembly, drive mechanism is equipped with the drive executor and gear connecting shaft that are transmission connection each other, is equipped with first gear and second gear in the both ends of gear connecting shaft respectively, is equipped with first rack in the part of first material frame corresponding to first gear, and first rack is engaged with first gear and connects, is equipped with second rack in the part of second material frame corresponding to second gear, and second rack is engaged with second gear and connects. Above all, through double gear / rack synchronous transmission, independent material frame design and double gear axial force balance etc. structure, the bearing capacity and stability of mechanism have been improved, flexible adaptation and error compensation have been realized, still possess safe redundancy and good durability.

Description

Technical Field

[0001] This utility model relates to the technical field of transfer mechanisms, and in particular to a heavy-duty transfer mechanism with dual-gear synchronous drive. Background Technology

[0002] In many industrial sectors, such as engineering machinery manufacturing, large equipment assembly, and logistics warehousing, precise and coordinated handling of heavy goods (typically weighing several tons to tens or even hundreds of tons) is frequently required. Current technology often employs a combination of servo motors, reducers, and ball screws to achieve this transfer. However, ball screws have revealed several drawbacks in practical applications. Firstly, their durability is poor. Due to the enormous loads generated by heavy goods, ball screws are prone to wear and fatigue cracks, leading to frequent component replacements and increased maintenance costs and downtime. Secondly, the load capacity of ball screws is relatively limited, making it difficult to stably support extremely heavy goods. When handling large items, the screw is prone to deformation or even breakage, posing serious safety hazards. Furthermore, their stability is also unsatisfactory. During high-speed operation or frequent start-stop cycles, vibrations and displacement deviations are likely to occur, failing to meet the requirements for precise handling of heavy goods.

[0003] With the continuous expansion of industrial production scale and the ongoing improvement of automation, higher requirements are being placed on the load-bearing capacity, stability, and durability of heavy-duty transfer mechanisms. Existing ball screw-based transfer solutions can no longer adapt to complex and changing working conditions and the ever-increasing demand for heavy-duty handling, necessitating a new type of transfer mechanism to solve these problems. Utility Model Content

[0004] To overcome the shortcomings mentioned above, this utility model aims to provide a technical solution that can solve the above problems.

[0005] This utility model provides a heavy-duty transfer mechanism with dual-gear synchronous drive, comprising:

[0006] The base assembly supports the entire heavy-duty transfer mechanism and is mounted on external equipment.

[0007] A rack assembly, slidably connected to a base assembly, is used to support the objects to be transferred; and

[0008] The drive mechanism is fixed to the base assembly and connected to the material rack assembly, thereby driving the material rack assembly to move along the base assembly;

[0009] The material rack assembly includes a first material rack and a second material rack that are independent of each other. The first material rack and the second material rack are slidably connected to the base assembly. The drive mechanism includes a drive actuator and a gear connecting shaft that are connected to each other. A first gear and a second gear are respectively provided at both ends of the gear connecting shaft. A first rack is provided at the part of the first material rack corresponding to the first gear, and the first rack is meshed with the first gear. A second rack is provided at the part of the second material rack corresponding to the second gear, and the second rack is meshed with the second gear.

[0010] Furthermore, both the first gear and the second gear are helical gears, and the inclination direction of the teeth of the first gear is opposite to that of the teeth of the second gear.

[0011] Furthermore, both the first rack and the second rack are helical racks. The inclination direction of the teeth of the first rack matches the inclination direction of the teeth of the first gear, and the inclination direction of the teeth of the second rack matches the inclination direction of the teeth of the second gear. Moreover, the inclination directions of the teeth of the first rack and the second rack are opposite.

[0012] Furthermore, the drive mechanism is also equipped with a speed reduction transmission device, which is installed on the base assembly. One end of the speed reduction transmission device is connected to the drive actuator, and the other end is connected to the gear connecting shaft, thereby driving the gear to rotate.

[0013] Furthermore, the drive mechanism is also provided with a drive support seat, which is fixedly connected to the base assembly, and a drive bearing is provided at the part of the drive support seat corresponding to the gear connecting shaft. The drive bearing is fixedly connected to the drive support seat and sleeved on the gear connecting shaft.

[0014] Furthermore, the drive mechanism is also provided with an adjustment component, which is used to adjust the height of the gear connecting shaft relative to the base assembly.

[0015] Furthermore: the adjustment assembly is provided with an adjustment base, a lifting seat and an adjustment bolt, wherein the adjustment base is fixedly connected to the base assembly, the lifting seat is movably connected to the adjustment base and can be raised and lowered in the vertical direction; the adjustment bolt is threaded through the lifting seat, and its top end abuts or is fixedly connected to the adjustment base, and the end of the lifting seat away from the adjustment bolt is fixedly connected to the adjustment plate of the speed reduction transmission device.

[0016] Furthermore, the base assembly is provided with a first guide rail and a second guide rail on both sides respectively. The first material rack is provided with a first slider at the position corresponding to the first guide rail, and the second material rack is provided with a second slider at the position corresponding to the second guide rail. The first slider and the first guide rail cooperate with each other, and the second slider and the second guide rail cooperate with each other to form a sliding connection.

[0017] Furthermore, it also includes a sensing component, which is provided with a limit switch and a switch stop, the limit switch being fixedly connected to the material rack assembly, and the switch stop being fixedly connected to the base assembly.

[0018] Compared with the prior art, the beneficial effects of this utility model are:

[0019] ① High load-bearing capacity and stability: The heavy-duty transfer mechanism of this utility model adopts a synchronous transmission structure of double gears / racks, which greatly improves the load-bearing capacity compared with the traditional ball screw. By rationally designing the module, tooth width, and other parameters of the gears and racks, it can stably bear heavy goods ranging from several tons to tens of tons. At the same time, the cooperation between the helical gears and helical racks, as well as the design of mutual balance of axial forces of the double gears, effectively avoids the movement and jamming of the transmission components, making the entire mechanism more stable during operation and ensuring the stability and safety of heavy goods handling.

[0020] ② Flexible Adaptation and Error Compensation: The rack assembly consists of independent first and second racks, each driven by a separate rack and pinion system. This independent structure allows for flexible adjustment based on the size and weight distribution of different goods, achieving load dispersion. During handling, if a slight deviation occurs on one rack, the other side can compensate for the error through independent transmission, improving adaptability to complex working conditions and solving the practical problem of adapting to multiple specifications.

[0021] ③ Safety Redundancy and Durability: The dual-gear synchronous drive provides a safety redundancy design. When one gear or rack fails, the other side can still maintain a certain carrying capacity, reducing the risk of production stoppage due to sudden equipment failure. In addition, the overall structure has been optimized, and high-strength materials are used to manufacture key components such as gears and racks. With good lubrication and protection measures, the durability of the mechanism is significantly improved, and the frequency and cost of maintenance are reduced.

[0022] ④ Precise Control and Efficient Adjustment: The drive actuator uses a servo motor, which can precisely adjust and control the speed and number of rotations of the gears, thereby achieving precise control over the moving speed and position of the rack assembly and meeting the needs of precise handling of heavy goods. Simultaneously, the adjustable components allow for easy adjustment of the height of the gear connecting shaft relative to the base assembly, thereby optimizing the meshing state of the gear and rack, ensuring transmission efficiency and stability, and improving the overall performance and applicability of the equipment.

[0023] Therefore, this utility model improves the load-bearing capacity and stability of the mechanism through the synchronous transmission of dual gears / racks, independent material rack design and dual gear axial force balance, etc., realizes flexible adaptation and error compensation, and also has safety redundancy and good durability.

[0024] Additional aspects and advantages of this invention will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention. Attached Figure Description

[0025] To more clearly illustrate the technical solutions in the embodiments of this utility model or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this utility model. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0026] Figure 1 This is a schematic diagram of the overall structure of this utility model;

[0027] Figure 2 This is a schematic diagram of the material rack assembly and drive mechanism of this utility model;

[0028] Figure 3 This is a schematic diagram of the material rack assembly and sensing assembly of this utility model;

[0029] Figure 4 This is a schematic diagram of the rack and gear meshing state of this utility model.

[0030] Figure 5 This is a schematic diagram of the gear connecting shaft and drive bearing of this utility model;

[0031] Figure 6 This is a schematic diagram of the structure of the adjustment component and the gear connecting shaft of this utility model.

[0032] The reference numerals and names in the figure are as follows:

[0033] 10 Base assembly; 11 First guide rail; 12 Second guide rail; 20 Material rack assembly; 21 First material rack; 22 First rack; 23 First slider; 24 Second material rack; 25 Second rack; 26 Second slider; 30 Drive mechanism; 31 Drive actuator; 32 Reduction transmission device; 33 Adjusting plate; 34 Drive support seat; 35 Drive bearing; 36 Gear connecting shaft; 37 First gear; 38 Second gear; 40 Adjusting assembly; 41 Adjusting base; 42 Lifting seat; 43 Adjusting bolt; 50 Sensing assembly; 51 Limit switch; 52 Switch stop. Detailed Implementation

[0034] The technical solutions in the embodiments of this utility model will be clearly and completely described below. Obviously, the described embodiments are only some embodiments of this utility model, and not all embodiments. Based on the embodiments of this utility model, all other embodiments obtained by those skilled in the art without creative effort are within the protection scope of this utility model.

[0035] Please see Figures 1 to 6 In this embodiment of the present invention, a heavy-duty transfer mechanism with dual-gear synchronous drive includes:

[0036] The base assembly 10 is used to support the entire heavy-duty transfer mechanism and is mounted on external equipment.

[0037] The rack assembly 20, slidably connected to the base assembly 10, is used to support the object to be transferred; and

[0038] The drive mechanism 30 is fixed to the base assembly 10 and is connected to the material rack assembly 20 for transmission, thereby driving the material rack assembly 20 to move along the base assembly 10;

[0039] The material rack assembly 20 includes a first material rack 21 and a second material rack 24 that are independent of each other. The first material rack 21 and the second material rack 24 are slidably connected to the base assembly 10. The drive mechanism 30 includes a drive actuator 31 and a gear connecting shaft 36 that are connected to each other. A first gear 37 and a second gear 38 are respectively provided at both ends of the gear connecting shaft 36. A first rack 22 is provided at the position of the first material rack 21 corresponding to the first gear 37, and the first rack 22 is meshed with the first gear 37. A second rack 25 is provided at the position of the second material rack 24 corresponding to the second gear 38, and the second rack 25 is meshed with the second gear 38.

[0040] Specifically, heavy-duty transfer mechanisms, with their high load-bearing capacity, strong motion synchronization, and stable operation, are widely used in scenarios requiring precise and coordinated handling of heavy goods (typically weighing from several tons to tens or even hundreds of tons). However, current technologies typically employ servo motors, reducers, and ball screws for transfer operations. The durability, load-bearing capacity, and stability of ball screws are relatively poor; therefore, improvements are necessary.

[0041] The heavy-duty transfer mechanism of this utility model, through the synchronous transmission structure of double gears / racks, can not only meet the basic requirements of "heavy-duty handling", but also achieve flexible adaptation, error compensation and safety redundancy through the coordinated movement of independent material racks on both sides, thereby improving the stability, load capacity and durability of the equipment.

[0042] Secondly, a first material rack 21 and a second material rack 24 are slidably connected to both sides of the base assembly 10. A drive mechanism 30 is installed in the middle of the base. The two sides of the drive mechanism 30 are driven by gears and racks to move the first material rack 21 and the second material rack 24 synchronously. The material rack assemblies 20 on both sides are independent of each other, using independent racks and gears for independent transmission. Its independent structure solves practical problems such as "load dispersion, error compensation, and multi-specification adaptation", while synchronous drive ensures the core coordinated motion requirements. The combination of the two enables the mechanism to stably transport heavy goods and adapt to complex and changing working conditions.

[0043] In addition, the drive actuator 31 can be a servo motor as described in the prior art, so as to achieve precise control of the gear speed and number of rotations.

[0044] like Figure 4 and Figure 5 As shown, preferably, both the first gear 37 and the second gear 38 are helical gears, and the inclination direction of the teeth of the first gear 37 is opposite to the inclination direction of the teeth of the second gear 38.

[0045] Specifically, both the first gear 37 and the second gear 38 are helical gears with their teeth extending in a spiral shape. The inclination direction of the teeth of the first gear 37 is opposite to that of the teeth of the second gear 38 (i.e., their spiral directions are opposite). When the drive actuator 31 drives the gear connecting shaft 36 to rotate, the axial force generated by the meshing of the first gear 37 and the first rack 22 is opposite in direction to the axial force generated by the meshing of the second gear 38 and the second rack 25. Since the first gear 37 and the second gear 38 are fixed to the same gear connecting shaft 36, their axial forces can balance each other, thereby achieving axial offset compensation during synchronous transmission of the two gears. This avoids axial movement of the gear connecting shaft 36 or transmission jamming caused by unilateral axial force, improving transmission stability.

[0046] like Figure 4 and Figure 5 As shown, preferably, the first rack 22 and the second rack 25 are both helical racks. The inclination direction of the teeth of the first rack 22 matches the inclination direction of the teeth of the first gear 37, and the inclination direction of the teeth of the second rack 25 matches the inclination direction of the teeth of the second gear 38. The inclination directions of the teeth of the first rack 22 and the second rack 25 are opposite.

[0047] Furthermore, both the first rack 22 and the second rack 25 are helical racks, with their teeth extending in a helical shape adapted to the corresponding gears. Specifically, the inclination direction of the teeth of the first rack 22 matches the inclination direction of the teeth of the first gear 37 (i.e., their helix angles are equal and their directions of rotation are the same), to achieve stable meshing transmission between the first gear 37 and the first rack 22; similarly, the inclination direction of the teeth of the second rack 25 matches the inclination direction of the teeth of the second gear 38 (i.e., their helix angles are equal and their directions of rotation are the same), to achieve stable meshing transmission between the second gear 38 and the second rack 25.

[0048] Since the teeth of the first gear 37 and the second gear 38 are inclined in opposite directions, the teeth of the first rack 22 and the second rack 25 are also inclined in opposite directions. This allows the axial force generated by the meshing of the first gear 37 and the first rack 22, and the axial force generated by the meshing of the second gear 38 and the second rack 25, to cancel each other out along the axial direction of the gear connecting shaft 36. This balances the axial load on the gear connecting shaft 36 and avoids wear of the transmission components or deviation of the mechanism due to the accumulation of axial force.

[0049] like Figures 4 to 6 As shown, preferably, the drive mechanism 30 is further provided with a speed reduction transmission device 32, which is installed on the base assembly 10. One end of the speed reduction transmission device 32 is connected to the drive actuator 31, and the other end is connected to the gear connecting shaft 36, thereby driving the gear to rotate.

[0050] Specifically, in order to further reduce the speed of the gear connecting shaft 36, a speed reduction transmission device 32 is preferably provided, which reduces the speed and increases the torque of the power output from the drive actuator 31. Furthermore, the speed reduction transmission device 32 can be a gear reducer from the prior art, such as the KAB77 reducer.

[0051] like Figure 5 As shown, preferably, the drive mechanism 30 is further provided with a drive support seat 34, which is fixedly connected to the base assembly 10, and a drive bearing 35 is provided at the part of the drive support seat 34 corresponding to the gear connecting shaft 36. The drive bearing 35 is fixedly connected to the drive support seat 34 and sleeved on the gear connecting shaft 36.

[0052] Specifically, to support the gear connecting shaft 36, it is preferable to provide two sets of drive support seats 34 and drive bearings 35 on both sides of the reduction transmission device 32 along the axial direction of the gear connecting shaft 36, so that the gear connecting shaft 36 passes through the drive bearings 35 and is supported by the drive support seats 34 in cooperation with the drive bearings 35. The drive bearings 35 are preferably existing mounted spherical bearings with a spherical outer ring structure, which can be adapted to the bearing seat with a spherical inner hole and has an automatic self-aligning function to optimize the rotational stability of the gear connecting shaft 36.

[0053] like Figures 4 to 6 As shown, preferably, the drive mechanism 30 is further provided with an adjustment component 40, which is used to adjust the height of the gear connecting shaft 36 relative to the base assembly 10.

[0054] Specifically, in order to adjust the meshing state between the gear and the rack, it is necessary to adjust the height between the gear and the base assembly 10, that is, to adjust the height of the gear connecting shaft 36 relative to the base assembly 10. Therefore, the adjustment component 40 can be set to adjust the height of the entire reduction transmission device 32 relative to the base assembly 10, thereby changing the gap between the gear and the rack and adjusting their meshing state.

[0055] like Figure 5 and Figure 6 As shown, preferably, the adjustment assembly 40 is provided with an adjustment base 41, a lifting seat 42 and an adjustment bolt 43, wherein the adjustment base 41 is fixedly connected to the base assembly 10, the lifting seat 42 is movably connected to the adjustment base 41 and can be raised and lowered in the vertical direction; the adjustment bolt 43 is threaded through the lifting seat 42, and its top end abuts against or is fixedly connected to the adjustment base 41, and the end of the lifting seat 42 away from the adjustment bolt 43 is fixedly connected to the adjustment plate 33 of the speed reduction transmission device 32.

[0056] Specifically, by rotating the adjusting bolt 43, the lifting seat 42 can be driven to rise and fall along the adjusting base 41, thereby adjusting the height of the reduction transmission device 32 relative to the base assembly 10. In order to adjust the height between the reduction transmission device 32 and the base assembly 10, and thus adjust the height of the gear connecting shaft 36 relative to the base assembly 10, it is preferable to fix an adjusting plate 33 to the reduction transmission device 32 and fix one end of the lifting seat 42 to the adjusting plate 33. Then, by rotating the adjusting bolt 43, the distance between the lifting seat 42 and the adjusting base 41 is changed, thereby adjusting the height between the reduction transmission device 32 and the base assembly 10.

[0057] Secondly, a round hole is provided on the adjusting plate 33, and a vertical elongated hole is provided on the adjusting base 41 corresponding to the round hole. A fastening bolt passes through the elongated hole and the round hole to detachably fix the adjusting base 41 and the adjusting plate 33. During adjustment, the fastening bolt is loosened to allow it to slide along the elongated hole. The adjusting bolt 43 is rotated to drive the lifting seat 42 to rise and fall, thereby adjusting the height of the reduction transmission device 32. After reaching the desired position, the fastening bolt is tightened to complete the fixation.

[0058] like Figures 1 to 4 As shown, preferably, the base assembly 10 has a first guide rail 11 and a second guide rail 12 on both sides, the first material rack 21 has a first slider 23 corresponding to the first guide rail 11, and the second material rack 24 has a second slider 26 corresponding to the second guide rail 12. The first slider 23 and the first guide rail 11 cooperate with each other, and the second slider 26 and the second guide rail 12 cooperate with each other to form a sliding connection.

[0059] Specifically, to optimize the sliding connection between the rack assembly 20 and the base assembly 10, a linear reciprocating motion structure, such as a combination of a linear guide and a slider, is preferably used. Furthermore, to facilitate the movement of heavy objects by the heavy-duty transfer mechanism, a linear guide with high load-bearing capacity is preferred.

[0060] Secondly, the sensing component 50 is equipped with two sets of limit switches 51 and corresponding switch blocks 52. The two sets of limit switches 51 are respectively fixed to the first material rack 21 and the second material rack 24, and the corresponding switch blocks 52 are fixed to the corresponding positions of the base component 10, so as to detect the movement stroke of the material racks on both sides respectively. However, in order to simplify the structure and save costs, only one set of limit switches 51 and switch blocks 52 can be set, and the movement position of the material rack component 20 can only be sensed in one set of material racks.

[0061] like Figure 2 and Figure 3 As shown, preferably, it also includes a sensing component 50, which is provided with a limit switch 51 and a switch block 52. The limit switch 51 is fixed to the material rack assembly 20, and the switch block 52 is fixed to the base assembly 10.

[0062] Specifically, the limit switch 51 moves synchronously with the material rack assembly 20, so that the trigger end of the limit switch 51 contacts the switch stop 52 and is triggered by the switch stop 52, causing the limit switch 51 to send a corresponding movement stop signal to the control center, so that the drive actuator 31 stops driving the material rack assembly 20.

[0063] In addition, in this embodiment, to meet the high load-bearing requirements of the heavy-duty transfer mechanism, the first gear 37, the second gear 38 and the corresponding first rack 22 and second rack 25 all adopt large-size tooth structures.

[0064] Specifically, the gear has a module of 6mm, a tooth width of 14mm (approximately 2.3 times the module), and a normal tooth thickness of 10mm. The corresponding rack has the same module as the gear, but its tooth width is slightly larger (15mm) to ensure contact stability during meshing. Furthermore, incorporating a helical gear design, the gear has a helix angle of 20°, and the rack teeth have the same helix angle as the corresponding gear, with the tooth surfaces hardened (reaching a hardness of HRC58-62).

[0065] Through the above-mentioned large-size tooth structure design, the contact area between the gear and the rack is increased by about 45% compared with the conventional small module structure, the tooth surface contact stress is reduced to below 800MPa, the tooth root bending stress is controlled within 350MPa, it can stably withstand a load of more than 25 tons, and after 1000 hours of continuous operation, the tooth surface wear is less than 0.1mm, effectively meeting the long-term transfer requirements of heavy goods.

[0066] It will be apparent to those skilled in the art that this invention is not limited to the details of the exemplary embodiments described above, and that it can be implemented in other specific forms without departing from the spirit or essential characteristics of this invention. Therefore, the embodiments should be considered exemplary and non-limiting in all respects, and the scope of this invention is defined by the appended claims rather than the foregoing description. Thus, it is intended that all variations falling within the meaning and scope of equivalents of the claims be included within this invention.

Claims

1. A heavy-duty transfer mechanism with dual-gear synchronous drive, characterized in that, include: The base assembly (10) is used to support the entire heavy-duty transfer mechanism and is mounted on external equipment; The rack assembly (20) is slidably connected to the base assembly (10) and is used to support the object to be transferred; as well as The drive mechanism (30) is fixed to the base assembly (10) and connected to the material rack assembly (20) for transmission, thereby driving the material rack assembly (20) to move along the base assembly (10); The material rack assembly (20) is provided with a first material rack (21) and a second material rack (24) that are independent of each other. The first material rack (21) and the second material rack (24) are slidably connected to the base assembly (10). The drive mechanism (30) is provided with a drive actuator (31) and a gear connecting shaft (36) that are connected to each other. A first gear (37) and a second gear (38) are provided at both ends of the gear connecting shaft (36). A first rack (22) is provided at the part of the first material rack (21) corresponding to the first gear (37), and the first rack (22) is meshed with the first gear (37). A second rack (25) is provided at the part of the second material rack (24) corresponding to the second gear (38), and the second rack (25) is meshed with the second gear (38).

2. The heavy-duty transfer mechanism with dual-gear synchronous drive according to claim 1, characterized in that, Both the first gear (37) and the second gear (38) are helical gears, and the inclination direction of the teeth of the first gear (37) is opposite to the inclination direction of the teeth of the second gear (38).

3. The heavy-duty transfer mechanism with dual-gear synchronous drive according to claim 2, characterized in that, Both the first rack (22) and the second rack (25) are helical racks. The tooth inclination direction of the first rack (22) matches the tooth inclination direction of the first gear (37), and the tooth inclination direction of the second rack (25) matches the tooth inclination direction of the second gear (38). The tooth inclination directions of the first rack (22) and the second rack (25) are opposite.

4. The heavy-duty transfer mechanism with dual-gear synchronous drive according to claim 1, characterized in that, The drive mechanism (30) is also provided with a speed reduction transmission device (32), which is installed on the base assembly (10). One end of the device is connected to the drive actuator (31), and the other end is connected to the gear connecting shaft (36), thereby driving the gear to rotate.

5. A heavy-duty transfer mechanism with dual-gear synchronous drive according to claim 1, characterized in that, The drive mechanism (30) is also provided with a drive support seat (34), which is fixed to the base assembly (10), and a drive bearing (35) is provided at the part of the drive support seat (34) corresponding to the gear connecting shaft (36). The drive bearing (35) is fixed to the drive support seat (34) and sleeved on the gear connecting shaft (36).

6. The heavy-duty transfer mechanism with dual-gear synchronous drive according to claim 1, characterized in that, The drive mechanism (30) is also provided with an adjustment component (40) for adjusting the height of the gear connecting shaft (36) relative to the base assembly (10).

7. A heavy-duty transfer mechanism with dual-gear synchronous drive according to claim 6, characterized in that, The adjustment assembly (40) is provided with an adjustment base (41), a lifting seat (42) and an adjustment bolt (43). The adjustment base (41) is fixed to the base assembly (10), and the lifting seat (42) is movably connected to the adjustment base (41) and can be raised and lowered in the vertical direction. The adjustment bolt (43) is threaded through the lifting seat (42), and its top end abuts or is fixedly connected to the adjustment base (41). The end of the lifting seat (42) away from the adjustment bolt (43) is fixed to the adjustment plate (33) of the speed reduction transmission device (32).

8. A heavy-duty transfer mechanism with dual-gear synchronous drive according to claim 1, characterized in that, The base assembly (10) has a first guide rail (11) and a second guide rail (12) on both sides respectively. The first material rack (21) has a first slider (23) corresponding to the first guide rail (11), and the second material rack (24) has a second slider (26) corresponding to the second guide rail (12). The first slider (23) and the first guide rail (11) cooperate with each other, and the second slider (26) and the second guide rail (12) cooperate with each other to form a sliding connection.

9. A heavy-duty transfer mechanism with dual-gear synchronous drive according to claim 1, characterized in that, It also includes a sensing component (50), which is provided with a limit switch (51) and a switch block (52). The limit switch (51) is fixed to the material rack assembly (20), and the switch block (52) is fixed to the base assembly (10).

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