Helical-toothed reduction gearbox and section steel straightener

Abstract

The utility model provides a kind of helical-tooth reduction gearbox and section steel straightening machine, belong to steel processing technical field, including box, input shaft and output shaft, first half axle and second half axle;Input shaft and output shaft parallel interval distribution and all rotationally connected in box, input helical gear is sleeved on input shaft, output helical gear is sleeved on output shaft. First half axle and second half axle are coaxially connected by magnetic force transmission structure and both are rotationally connected in box, first helical gear meshing with input helical gear is sleeved on first half axle, second helical gear is sleeved on second half axle, and second helical gear and output helical gear are drivenly connected by at least a pair of reduction helical gear. The helical-tooth reduction gearbox and section steel straightening machine provided by the utility model can alleviate the problem of gear grinding and gear scanning caused by frequent load changes of the reduction gearbox, and improve the service life of the gear.

Description

Technical Field

[0001] This utility model belongs to the field of steel processing technology, specifically relating to a helical gear reducer and a steel profile straightening machine. Background Technology

[0002] After the profiles are rolled, they need to go through a straightening and leveling process to achieve the purpose of profile shaping and eliminating internal stress. Currently, the commonly used profile straightening equipment is the gantry multi-roll straightener. This type of straightener is usually powered by an electric motor, and the power of the motor is transmitted to the straightening rolls through a gearbox. The gearbox plays the role of reducing speed and increasing torque to ensure sufficient straightening power.

[0003] In existing technologies, the gearboxes used in steel section straightening machines are mostly three-stage reduction gear drives. Due to the unpredictable deformation defects that occur after steel section rolling, the load on the straightening rollers is greater where the deformation is large and lesser where the deformation is small. This frequent load changes cause tooth wear between the reduction gear pairs within the gearbox, especially noticeable in the primary drive gear pair due to the high input speed. In severe cases, sudden changes in tooth surface load can even lead to tooth shaving, a problem that urgently needs to be addressed. Utility Model Content

[0004] This utility model provides a helical gear reducer and a steel profile straightening machine, aiming to solve the problem of gear grinding and scorching caused by frequent load changes in the reducer and improve gear life.

[0005] To achieve the above objectives, the technical solution adopted by this utility model is as follows: Firstly, a helical gear reducer is provided, comprising: The housing has an internal sealed space suitable for containing lubricating oil; The input shaft and the output shaft are parallel and spaced apart, and both are rotatably connected to the housing. The input shaft is fitted with an input helical gear, and one end of the input shaft is sealed and extends out of the housing to connect to the rotational power source. The output shaft is fitted with an output helical gear, and one end of the output shaft is sealed and extends out of the housing to connect to the load. The first half-shaft and the second half-shaft are coaxially connected by a magnetic transmission structure and rotate together in the housing. The first half-shaft is fitted with a first helical gear that meshes with the input helical gear, and the second half-shaft is fitted with a second helical gear. The second helical gear and the output helical gear mesh directly or are connected by transmission through at least one pair of reduction helical gears.

[0006] In conjunction with the first aspect, in one possible implementation, the magnetic drive structure includes: The first connector has a cavity formed at the end of the first half-axis and facing the second half-axis, and a plurality of first magnets are distributed circumferentially on the periphery of the cavity. The second connector is located on the second half-shaft. One end of the second connector extends into the cavity and is provided with several second magnets arranged circumferentially at intervals. Each of the second magnets corresponds to each of the first magnets and forms a magnetic coupling force, and the first half-axis drives the second half-axis to rotate based on the magnetic coupling force.

[0007] In some embodiments, the bottom center of the concave cavity is provided with a frustum, and the end center of the second connector has a conical cavity suitable for coaxial insertion of the frustum; wherein the frustum and the conical cavity have the same taper and are rotated together.

[0008] For example, a connecting hole is provided at the center of the end of the second half-shaft away from the conical cavity, and a bearing platform is formed between the bottom of the connecting hole and the bottom of the conical cavity; an elastic connector is provided in the connecting hole, one end of the elastic connector passes through the bearing platform and is connected to the conical platform; the elastic connector is used to apply axial elastic tension between the first connector and the second connector.

[0009] For example, flexible connectors include: The tensioning rod has one end forming an operating head and the other end passing through the support platform to connect to the frustum. The thrust bearing, ring-type tensioning rod, and axially presses against the bearing platform; The disc spring is sleeved on the tensioning rod and located between the operating head and the thrust bearing.

[0010] In one possible implementation, the center of the truncated cone has a threaded hole, and the tensioning rod passes through the bearing platform to form a threaded segment, which is then screwed into the threaded hole for fixation.

[0011] In some embodiments, a wear-resistant conical sleeve is provided between the cavity wall of the conical cavity and the peripheral wall of the conical frustum.

[0012] For example, an intermediate shaft is rotatably connected inside the housing, and a third helical gear and a fourth helical gear are fitted around the intermediate shaft at intervals along its circumference; the third helical gear meshes with the second helical gear, and the fourth helical gear meshes with the output helical gear.

[0013] For example, the transmission ratios between the input helical gear and the first helical gear, the second helical gear and the third helical gear, and the third helical gear and the output helical gear increase sequentially and are all greater than one.

[0014] The beneficial effects of the helical gear reducer provided by this utility model are as follows: Compared with the prior art, the helical gear reducer of this utility model forms a sealed space filled with lubricating oil inside the gearbox, which can lubricate and cool the helical gear meshing transmission; compared with spur gears, the use of helical gear transmission can increase the tooth surface contact area between the transmission gear pairs, thereby improving the transmission load capacity. During operation, the rotational power source, such as a motor, drives the input shaft to rotate. The power is transmitted to the first half-shaft through the meshing of the input helical gear and the first helical gear, and then transmitted from the first half-shaft to the second half-shaft through the magnetic transmission structure. The second helical gear mounted on the second half-shaft transmits the power directly or indirectly through at least one pair of reduction helical gears to the output helical gear, and finally from the output shaft to the load, such as the straightening roller of a steel profile straightening machine. Through the above multi-stage transmission, the power is reduced in speed and increased in torque, thereby meeting the power requirements of the load.

[0015] Because a magnetic drive structure is used between the first and second half-shafts, a flexible angular difference can be formed between them based on load changes. Compared to the rigid connection method in existing technologies where two gears are mounted on the same shaft, this not only alleviates gear wear caused by load changes through the flexible angular difference between the first and second half-shafts, but also provides flexible buffering for changes in tooth surface load, thereby avoiding tooth shaving caused by sudden changes in tooth surface load and thus improving the life of helical gears. In addition, the magnetic drive structure also has an overload protection function, which can prevent damage to the rotating power source under excessive load.

[0016] Secondly, this utility model embodiment also provides a steel profile straightening machine, including the above-mentioned helical gear reducer.

[0017] The beneficial effects of the steel profile straightening machine provided by this utility model are as follows: Compared with the prior art, the steel profile straightening machine of this utility model adopts the above-mentioned helical gear reducer. Through the magnetic transmission structure, a flexible rotation angle difference is established between the first half shaft and the second half shaft, thereby providing flexible buffer for changes in tooth surface load, alleviating the problems of tooth grinding and tooth swirl caused by load changes, which is conducive to improving gear life and thus improving the working stability of the helical gear reducer. Attached Figure Description

[0018] Figure 1 A cross-sectional view of the helical gear reducer provided in an embodiment of this utility model; Figure 2 for Figure 1 A magnified schematic diagram of the local structure at point A; Figure 3 For along Figure 2 Schematic diagram of the cross-sectional structure of the middle BB line.

[0019] In the diagram: 10, housing; 20, input shaft; 21, input helical gear; 30, output shaft; 31, output helical gear; 40, first half-shaft; 41, first helical gear; 50, second half-shaft; 51, second helical gear; 52, connecting hole; 53, support platform; 54, elastic connector; 541, tensioning rod; 542, thrust bearing; 543, disc spring; 60, magnetic transmission structure; 61, first connecting body; 611, cavity; 612, first magnet; 613, frustum; 614, threaded hole; 62, second connecting body; 621, second magnet; 622, conical cavity; 70, wear-resistant conical sleeve; 80, intermediate shaft; 81, third helical gear; 82, fourth helical gear. Detailed Implementation

[0020] To make the technical problems, technical solutions, and beneficial effects of this utility model clearer, the present utility model will be further described in detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative of the present utility model and are not intended to limit the present utility model.

[0021] It should be noted that when an element is referred to as being "set on" or "connected to" another element, it can be directly on or indirectly on the other element. It should be understood that the terms "upper," "lower," "front," "rear," "top," "bottom," "inner," and "outer," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings, and are only for the convenience of describing this application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this application. 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 application, "multiple" or "several" means two or more, unless otherwise explicitly specified.

[0022] In existing technologies, the gearboxes used in steel section straightening machines are mostly three-stage spur gear drives. For example, for the leveling and straightening of H-beams, a gantry nine-roll straightening machine is commonly used, and the gearbox of the straightening machine uses a three-stage spur gear drive. With the increasing market requirements for the structural strength of H-beams, the failure rate of the gearbox is very high during the straightening operation of newly developed H-beam specifications such as 428×407, British Standard 254×254, and British Standard 356×406, especially the tooth shaving problem of the primary and secondary transmission gears.

[0023] In the process of developing this utility model, the applicant, based on actual on-site conditions, found that a three-stage transmission is insufficient for straightening high-strength steel profiles. This is because, with increasing load, the large single-stage transmission ratio in a three-stage transmission results in excessive tooth surface load, especially in the primary transmission section, where both the load and speed are high, leading to tooth shaving. While increasing the number of transmission stages can reduce the single-stage transmission ratio, a higher number of stages requires more space inside the gearbox, increasing the space occupied by the gearbox and significantly impacting the overall layout of the production site. Therefore, simply increasing the number of transmission stages is not a practical solution.

[0024] Please refer to the following: Figures 1 to 3 The helical gear reducer provided by this utility model will now be described. The helical gear reducer includes a housing 10, an input shaft 20 and an output shaft 30, a first half-shaft 40 and a second half-shaft 50; the housing 10 has a sealed space inside suitable for containing lubricating oil.

[0025] The input shaft 20 and the output shaft 30 are parallel and spaced apart, and are both rotatably connected inside the housing 10. The input shaft 20 is fitted with an input helical gear 21, and one end of the input shaft 20 is sealed and extends out of the housing 10 to connect to a rotational power source. The output shaft 30 is fitted with an output helical gear 31, and one end of the output shaft 30 is sealed and extends out of the housing 10 to connect to a load.

[0026] The first half-shaft 40 and the second half-shaft 50 are coaxially connected by a magnetic transmission structure 60 and rotate together within the housing 10. The first half-shaft 40 is fitted with a first helical gear 41 that meshes with the input helical gear 21, and the second half-shaft 50 is fitted with a second helical gear 51. The second helical gear 51 and the output helical gear 31 directly mesh or are connected by at least one pair of reduction helical gears.

[0027] It should be noted that in this embodiment, the input helical gear 21, output helical gear 31, first helical gear 41, second helical gear 51, and each reduction helical gear all adopt a helical tooth structure. Therefore, there will be axial force between the meshing gears. To ensure the stability of the transmission structure, the input shaft 20 is rotatably connected to the housing 10 on both sides of the input helical gear 21 via tapered roller bearings arranged back-to-back or face-to-face. Similarly, the ends of the first half-shaft 40 and the second half-shaft 50 that are far apart from each other are connected to the housing 10 via tapered roller bearings. Both ends of the output shaft 30 and each reduction helical gear axle are connected to the housing 10 via a pair of tapered roller bearings. The use of tapered roller bearings ensures the axial load-bearing capacity of each shaft. The housing 10 is provided with removable bearing covers corresponding to each tapered roller bearing, thereby facilitating disassembly and maintenance.

[0028] In this embodiment, since both the input shaft 20 and the output shaft 30 need to pass through the wall of the housing 10, in order to ensure that a sealed space can be formed inside the housing 10, sealing rings or oil seals can be provided at the parts where the input shaft 20 and the output shaft 30 pass through the housing wall to achieve a sealed connection, thereby preventing the lubricating oil added inside the housing 10 from leaking outward.

[0029] It should be explained that, in this embodiment, the lubricating oil added to the housing 10 should at least submerge part of the magnetic drive structure 60. The lubricating oil cools the magnetic drive structure 60, preventing overheating caused by magnetic coupling and affecting its transmission stability.

[0030] Specifically, in this embodiment, the input shaft 20 is preferably located at the bottom of the housing 10. In this way, the lubricating oil added to the housing 10 comes into contact with the input helical gear 21 sleeved on the input shaft 20. Since the rotation speed of the input helical gear 21 is not reduced, the high-speed rotation of the input helical gear 21 can carry the lubricating oil, so that all areas inside the housing 10 can obtain the splash lubrication effect of the lubricating oil.

[0031] In this embodiment, the connection between each helical gear and the corresponding shaft can be achieved by using a key connection to restrict rotational freedom, a snap ring or a limiting platform for axial positioning, or other forms of limiting structures. As this is prior art, no specific limitation is made here.

[0032] The helical gear reducer provided in this embodiment, compared with the prior art, forms a sealed space filled with lubricating oil inside the housing 10, which can lubricate and cool the helical gear meshing transmission. Compared with spur gears, the use of helical gear transmission can increase the tooth surface contact area between the transmission gear pairs, thereby improving the transmission load capacity. During operation, the rotational power source, such as a motor, drives the input shaft 20 to rotate. The power is transmitted to the first half-shaft 40 through the meshing of the input helical gear 21 and the first helical gear 41, and then transmitted from the first half-shaft 40 to the second half-shaft 50 through the magnetic transmission structure 60. The second helical gear 51, which is mounted on the second half-shaft 50, transmits the power directly or indirectly through at least one pair of reduction helical gears to the output helical gear 31. Finally, the power is transmitted from the output shaft 30 to the load, such as the straightening roller of a steel straightening machine. Through the above multi-stage transmission, the power is reduced in speed and increased in torque, thereby meeting the power requirements of the load.

[0033] Because a magnetic drive structure 60 is used between the first half-shaft 40 and the second half-shaft 50, a flexible angle difference can be formed between them based on load changes. Compared to the rigid connection method in the prior art where two gears are mounted on the same shaft, this not only alleviates the gear wear problem caused by load changes through the flexible angle difference between the first half-shaft 40 and the second half-shaft 50, but also provides flexible buffering for changes in tooth surface load, thereby avoiding tooth shaving problems caused by sudden changes in tooth surface load and thus improving the life of helical gears. In addition, the magnetic drive structure 60 also has an overload protection function, which can prevent damage to the rotating power source under excessive load.

[0034] In some embodiments, see Figure 2 and Figure 3 The magnetic drive structure 60 includes a first connector 61 and a second connector 62. The first connector 61 is located on the first half-shaft 40 and forms a cavity 611 at its end facing the second half-shaft 50. A plurality of first magnets 612 are distributed circumferentially on the periphery of the cavity 611. The second connector 62 is located on the second half-shaft 50. One end of the second connector 62 extends into the cavity 611 and is circumferentially arranged with a plurality of second magnets 621. Each second magnet 621 corresponds to each first magnet 612 and forms a magnetic coupling force. The first half-shaft 40 drives the second half-shaft 50 to rotate based on the magnetic coupling force.

[0035] The first magnet 612 and the second magnet 621 can be made of neodymium boron iron magnets to ensure sufficient magnetic force. Each first magnet 612 and the corresponding second magnet 621 are aligned radially along the cavity 611, and the magnetic poles of the corresponding first magnet 612 and the second magnet 621 are opposite in direction.

[0036] In the initial equilibrium state, each of the first magnets 612 and each of the second magnets 621 are aligned one-to-one. At this time, the magnetic forces generated between the two magnetic poles of each first magnet 612 and its opposite and adjacent second magnets 621 can cancel each other out.

[0037] When the first half-shaft 40 starts to rotate, the first magnet 612 and the second magnet 621 begin to deflect. During the deflection process, the distance between the two magnetic poles of the first magnetic pole and the two magnetic poles of the corresponding second magnetic pole changes. Therefore, the magnetic force of the second magnetic pole on the first magnetic pole is no longer balanced, thereby driving the second half-shaft 50 with load to start rotating with the first half-shaft 40.

[0038] When the first magnet 612 deflects to a position close to the center of the second magnet 621, the total driving force of each first magnet 612 on each second magnet 621 reaches its maximum. If the load continues to increase at this time, the first magnet 612 will rotate past the middle position of the second magnet 621 and begin to pair with the next second magnet 621, thereby achieving overload protection.

[0039] The transmission method using magnetic coupling described above is the same as the principle of magnetic couplings in the prior art, and will not be described in detail here. In this embodiment, the magnetic transmission structure 60 is intended to adapt the angular deviation of the first half-shaft 40 and the second half-shaft 50 to changes in load. This avoids the problem of excessive friction or even collision caused by sudden load changes on the meshing tooth surfaces (the probability of collision is relatively high due to the presence of tooth backlash). It not only provides overload protection, but more importantly, it can cope with frequently changing loads.

[0040] For some possible implementations, please refer to [link / reference]. Figure 2 The cavity 611 has a truncated cone 613 at its bottom center, and the end center of the second connecting body 62 has a conical cavity 622 suitable for coaxial insertion of the truncated cone 613. The truncated cone 613 and the conical cavity 622 have the same taper and are rotatably fitted together. The fit between the truncated cone 613 and the conical cavity 622 ensures the coaxiality of the connection between the first half-shaft 40 and the second half-shaft 50, making them a single unit. This avoids the radial runout problem that can easily occur when the first half-shaft 40 and the second half-shaft 50 are connected solely through rotatable parts with the housing 10, thus ensuring the operational stability of the first gear and the second gear.

[0041] In addition, considering the requirement that the first half-shaft 40 and the second half-shaft 50 change their rotation angles based on load changes, it is necessary to form a rotational fit between the frustum 613 and the cone cavity 622. Specifically, the rotational fit can adopt the traditional shaft and sleeve rotational fit method to ensure structural compactness.

[0042] Specifically, such as Figure 2 As shown, in this embodiment, the second half-shaft 50 is provided with a connecting hole 52 at the center of the end opposite to the conical cavity 622, and a support platform 53 is formed between the bottom of the connecting hole 52 and the bottom of the conical cavity 622; an elastic connector 54 is provided in the connecting hole 52, and one end of the elastic connector 54 passes through the support platform 53 and is connected to the conical truncated cone 613; the elastic connector 54 is used to apply axial elastic tension between the first connector 61 and the second connector 62.

[0043] By fastening the frustum 613 through the elastic connector 54 through the support platform 53, an elastic axial tension can be obtained between the first half-shaft 40 and the second half-shaft 50. This not only prevents the frustum 613 from coming out of the cone cavity 622 and ensures the reliability of the connection between the first half-shaft 40 and the second half-shaft 50, but also prevents the frustum 613 from exerting too much force on the cavity wall of the cone cavity 622, which would prevent the frustum 613 from being unable to rotate relative to the cone cavity 622.

[0044] As one specific embodiment of the aforementioned elastic connector 54, please refer to Figure 2The elastic connector 54 includes a tensioning rod 541, a thrust bearing 542, and a disc spring 543. One end of the tensioning rod 541 forms an operating head, and the other end passes through the support platform 53 and connects to the truncated cone 613. The thrust bearing 542 is sleeved around the tensioning rod 541 and axially presses against the support platform 53. The disc spring 543 is sleeved on the tensioning rod 541 and is located between the operating head and the thrust bearing 542.

[0045] By setting the thrust bearing 542, the tensioning link 541 can rotate together with the cone 613 while providing axial support force, avoiding direct contact between the operating head and the bearing platform 53, which would affect the flexible rotation of the cone 613 in the cone cavity 622. On this basis, the disc spring 543 is used to provide axial elastic force, which is more compact than other types of elastic components.

[0046] It should be noted that, as Figure 2 As shown, the center of the aforementioned truncated cone 613 is provided with a threaded hole 614. The tensioning connecting rod 541 passes through the bearing platform 53 to form a threaded section, which is screwed and fixed to the threaded hole 614. The operating head can be a round head structure with a slot in the center suitable for inserting tools such as Allen wrenches. By rotating the operating head, the depth of the threaded section screwed into the threaded hole 614 can be adjusted, thereby adjusting the elastic force applied to the operating head by the disc spring 543.

[0047] In some embodiments, such as Figure 2 As shown, a wear-resistant conical sleeve 70 is provided between the cavity wall of the conical cavity 622 and the peripheral wall of the conical frustum 613. The wear-resistant conical sleeve 70 can be a copper sleeve, and its surface is provided with an oil groove or oil pit for storing oil. Lubricating oil can enter the oil groove or oil pit to lubricate the rotating mating surfaces, thereby reducing friction and improving rotational flexibility.

[0048] It should be understood that, based on the connection method of the first half-shaft 40 and the second half-shaft 50, the power transmission between the two depends on the dual effects of the circumferential friction of the wear-resistant tapered sleeve 70 and the magnetic coupling force between the first magnet 612 and the second magnet 621. Among them, the magnetic coupling force plays the main role, while the circumferential friction force plays the auxiliary role of transmission, thereby ensuring sufficient load performance.

[0049] Optionally, see Figure 1 In this embodiment, an intermediate shaft 80 is rotatably connected inside the housing 10. A third helical gear 81 and a fourth helical gear 82 are spaced apart along the circumference of the intermediate shaft 80. The third helical gear 81 meshes with the second helical gear 51, and the fourth helical gear 82 meshes with the output helical gear 31. By utilizing the first and fourth helical gears 81 and 82 on the intermediate shaft 80, a three-stage reduction can be achieved between the input helical gear 21 and the output helical gear 31, improving the space utilization within the housing 10 and avoiding the problem of excessively large single-stage transmission ratios.

[0050] It should be understood that the meshing of the third helical gear 81 with the second helical gear 51 can be considered as a pair of reduction helical gears, and the meshing of the fourth helical gear 82 with the output helical gear 31 can also be considered as a pair of reduction helical gears; this is equivalent to a two-stage reduction from the second helical gear 51 to the output helical gear 31.

[0051] It should be noted that in this embodiment, the transmission ratios between the input helical gear 21 and the first helical gear 41, the second helical gear 51 and the third helical gear 81, and the third helical gear 81 and the output helical gear 31 increase sequentially and are all greater than one. Since the input helical gear 21 has the highest rotational speed, and the higher the rotational speed, the more sensitive it is to load changes, it is not advisable to use an excessively high transmission ratio. Therefore, the largest single-stage transmission ratio is arranged at the very end of the transmission route, namely the output helical gear 31 and the fourth helical gear 82. This can, to a certain extent, reduce the wear and collision problems of the meshing tooth surfaces caused by load changes and improve gear life.

[0052] Based on the same inventive concept, combined with Figures 1 to 3 It is understood that this application also provides a steel profile straightening machine, including the above-mentioned helical gear reducer.

[0053] Compared with the prior art, the steel straightening machine provided in this embodiment adopts the above-mentioned helical gear reducer. When the steel is straightened, the rotational power source, such as a motor, drives the input shaft 20 to rotate. The power is transmitted to the first half-shaft 40 through the meshing of the input helical gear 21 and the first helical gear 41. Then, it is transmitted from the first half-shaft 40 to the second half-shaft 50 through the magnetic transmission structure 60. The second helical gear 51, which is mounted on the second half-shaft 50, transmits the power directly or indirectly through at least one pair of reduction helical gears to the output helical gear 31. Finally, it is transmitted from the output shaft 30 to the load, such as the straightening roller of the steel straightening machine. Through the above-mentioned multi-stage transmission, the power is reduced and the torque is increased, thereby meeting the power requirements of the load.

[0054] Because a magnetic drive structure 60 is used between the first half-shaft 40 and the second half-shaft 50, a flexible angle difference can be formed between them based on load changes. Compared to the rigid connection method in the prior art where two gears are mounted on the same shaft, this not only alleviates the gear wear problem caused by load changes through the flexible angle difference between the first half-shaft 40 and the second half-shaft 50, but also provides flexible buffering for changes in tooth surface load, thereby avoiding tooth shaving problems caused by sudden changes in tooth surface load and thus improving the life of helical gears. In addition, the magnetic drive structure 60 also has an overload protection function, which can prevent damage to the rotating power source under excessive load.

[0055] The above description is only a preferred embodiment of the present utility model and is not intended to limit the present utility model. Any modifications, equivalent substitutions and improvements made within the spirit and principles of the present utility model should be included within the protection scope of the present utility model.

Claims

1. A helical gear reducer, characterized in that, include: The housing has an internal sealed space suitable for containing lubricating oil; The input shaft and the output shaft are parallel and spaced apart, and both are rotatably connected to the housing. The input shaft is fitted with an input helical gear, and one end of the input shaft is sealed and passes through the housing to connect to a rotational power source. The output shaft is fitted with an output helical gear, and one end of the output shaft is sealed and passes through the housing to connect to a load. The first half-shaft and the second half-shaft are coaxially connected by a magnetic transmission structure and rotate together within the housing. The first half-shaft is fitted with a first helical gear that meshes with the input helical gear, and the second half-shaft is fitted with a second helical gear. The second helical gear and the output helical gear mesh directly or are connected by at least one pair of reduction helical gears.

2. The helical gear reducer as described in claim 1, characterized in that, The magnetic drive structure includes: A first connector is provided at the end of the first half-axis and facing the second half-axis to form a cavity, and a plurality of first magnets are distributed circumferentially at intervals on the periphery of the cavity. A second connector is provided on the second half-shaft. One end of the second connector extends into the cavity and is provided with a plurality of second magnets arranged circumferentially at intervals. Each of the second magnets corresponds to each of the first magnets and forms a magnetic coupling force, and the first half-shaft drives the second half-shaft to rotate based on the magnetic coupling force.

3. The helical gear reducer as described in claim 2, characterized in that, The bottom center of the concave cavity is provided with a frustum, and the end center of the second connector has a conical cavity suitable for coaxial insertion of the frustum; wherein the frustum and the conical cavity have the same taper and are rotated together.

4. The helical gear reducer as described in claim 3, characterized in that, The second half-shaft has a connecting hole at the center of its end opposite to the conical cavity, and a support platform is formed between the bottom of the connecting hole and the bottom of the conical cavity; an elastic connector is provided in the connecting hole, and one end of the elastic connector passes through the support platform and is connected to the conical platform; the elastic connector is used to apply axial elastic tension between the first connector and the second connector.

5. The helical gear reducer as described in claim 4, characterized in that, The elastic connector includes: The tensioning rod has one end forming an operating head and the other end passing through the support platform and connecting to the frustum. A thrust bearing is fitted around the tensioning connecting rod and axially presses against the bearing platform. A disc spring is sleeved on the tensioning connecting rod and located between the operating head and the thrust bearing.

6. The helical gear reducer as described in claim 5, characterized in that, The cone has a threaded hole at its center, and the tensioning rod passes through the support platform to form a threaded section, which is then screwed into the threaded hole for fixation.

7. The helical gear reducer as described in claim 3, characterized in that, A wear-resistant conical sleeve is provided between the cavity wall of the conical cavity and the peripheral wall of the conical frustum.

8. The helical gear reducer as described in any one of claims 1-7, characterized in that, An intermediate shaft is rotatably connected inside the housing, and a third helical gear and a fourth helical gear are fitted on the intermediate shaft at intervals along its axial direction; the third helical gear meshes with the second helical gear, and the fourth helical gear meshes with the output helical gear.

9. The helical gear reducer as described in claim 8, characterized in that, The transmission ratios between the input helical gear and the first helical gear, the second helical gear and the third helical gear, and the fourth helical gear and the output helical gear increase sequentially and are all greater than one.

10. A steel profile straightening machine, characterized in that, Including the helical gear reducer as described in any one of claims 1-9.

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