A continuously variable speed ratio shifting device and an asynchronous rolling mill

Abstract

The application discloses a stepless speed ratio shifting device and an asynchronous rolling mill, and relates to the field of rolling equipment, to solve the problem that the transmission rolling mill needs to stop rotating during shifting. The shifting device comprises a first driving structure, a first transmission worm connected with the first driving structure in transmission, a first output shaft connected with the first transmission worm in transmission, and a first transmission shaft and a second output shaft which are both rotatably supported on a box body. The first output shaft is connected with an upper roller in transmission. A second transmission worm of a shifting mechanism is connected with the first transmission worm in transmission, and the rotation axes of the two are perpendicular to each other. A second driving structure is connected with the second transmission worm, and drives the second transmission worm to move in a direction parallel to the axial direction of the first transmission worm. The first transmission shaft is provided with a first shifting bevel gear connected with the second transmission worm in transmission and a first transmission bevel gear connected with a second transmission bevel gear on the second output shaft in transmission. The second output shaft is opposite to the first output shaft in rotation direction and parallel to the first output shaft in axial direction, and the second output shaft is connected with a lower roller in transmission.

Description

Technical Field

[0001] This invention relates to the field of rolling equipment technology, specifically to a continuously variable speed ratio shifting device and an asynchronous rolling mill. Background Technology

[0002] Asynchronous rolling mills employ asynchronous rolling methods. During the composite rolling of dissimilar metals, the upper and lower rolls rotate at different speeds in contact with the strip. By setting different rolling speed ratios, the cooperative deformation capability of the strip can be improved, and problems such as rolling shape defects and interface cracking can be solved.

[0003] Currently, traditional asynchronous rolling mills mainly achieve asynchronous rolling by directly connecting two three-phase motors to two rolls via a coupling, and controlling the speed of the two three-phase motors with a PLC to achieve the target speed ratio; or by using a mechanical graded speed change mechanism, which uses gear sets to switch between a few fixed speed ratios for discrete output. The problems with this approach are: According to the mechanical characteristic curve of the motor, the speed will change when the load changes. There is a problem of inconsistent friction between the upper and lower rolls and the upper and lower surfaces of the plate during the operation of the rolling mill, which causes the load of the upper and lower rolls to be different, thus changing the speed and making it impossible to complete the entire asynchronous rolling process under a constant speed ratio.

[0004] Mechanical graded speed change mechanisms can only perform gear shifting operations after the mill has stopped and unloaded. Each start-stop operation can only correspond to a single fixed speed ratio, making it impossible to change the speed ratio in real time according to the material deformation state during a single rolling pass and achieve continuous speed ratio. For strip and plate composite processes that require multiple rolling passes and where the optimal speed ratio for each pass may be different and not discrete, frequent shutdowns and gear shifting severely disrupt production continuity, resulting in low efficiency in the rolling process. Summary of the Invention

[0005] The purpose of this invention is to provide a continuously variable speed ratio shifting device and an asynchronous rolling mill to ensure the real-time and continuous shifting during rolling, as well as the stability of the rotational speed of the asynchronous rolling mill during operation, thereby improving rolling efficiency.

[0006] To achieve the above objectives, the present invention provides the following technical solution: In a first aspect, the present invention provides a continuously variable transmission (CVT) gear shifting device, comprising: Box; The first drive structure has its drive end rotatably supported by the housing. The first transmission worm is connected to the drive end of the first drive structure. The first transmission worm is rotatably supported on the housing. The first drive structure is used to drive the first transmission worm to rotate. The first output shaft meshes with the first transmission worm gear for transmission. The first output shaft is rotatably supported on the housing. The first output shaft is used to connect with the upper roller transmission. The shifting mechanism has a second transmission worm and a second drive structure. The second transmission worm meshes with the first transmission worm gear, and the rotation axis of the first transmission worm intersects with the rotation axis of the second transmission worm. The drive end of the second drive structure is connected to one end of the second transmission worm. The second drive structure is used to drive the second transmission worm to move in a direction parallel to the axis of the first transmission worm. The first drive shaft is rotatably supported on the housing, and a first shift bevel gear and a first transmission bevel gear are coaxially arranged on the first drive shaft. The first shift bevel gear meshes with the worm portion on the second transmission worm for transmission. The second output shaft has a second transmission bevel gear that meshes with the first transmission bevel gear. The second output shaft is rotatably supported by the housing, and the rotation direction of the second output shaft is opposite to that of the first output shaft. The axial direction of the first output shaft is parallel to that of the second output shaft. The second output shaft is used to connect with the lower roller drive.

[0007] Optionally, in the above continuously variable transmission (CVT) gear shifting device, the ratio of the rotational speed of the first output shaft to the rotational speed of the second output shaft is 0.7 to 1.3.

[0008] Optionally, the continuously variable transmission (CVT) further includes: The second drive shaft is rotatably supported on the housing. The second drive shaft and the first drive shaft are axially symmetrically distributed relative to the second drive worm. The second drive shaft is coaxially equipped with a second shift bevel gear and a third drive bevel gear. The second shift bevel gear meshes with the worm portion on the second drive worm, and the third drive bevel gear meshes with the fourth drive bevel gear on the second output shaft.

[0009] Optionally, in the above continuously variable transmission (CVT) gear shifting device, the first shift bevel gear and the second shift bevel gear have the same structure, and the bevel angle of the first shift bevel gear is 45°~60°.

[0010] Optionally, in the above continuously variable transmission (CVT) gear shifting device, the small end of the first shift bevel gear and the small end of the second shift bevel gear both face the second transmission worm, and the large end of the first shift bevel gear and the large end of the second shift bevel gear both face the second output shaft. Alternatively, the small ends of the first and second shift bevel gears both face the second output shaft, and the large ends of the first and second shift bevel gears both face the second transmission worm.

[0011] Optionally, in the above-mentioned continuously variable transmission (CVT) gear shifting device, the second drive structure includes: The telescopic rod is fixedly connected to one end of the second transmission worm gear, and the telescopic direction of the telescopic rod is parallel to the axial direction of the first transmission worm gear. The driving component is connected to the telescopic rod and is used to drive the telescopic rod to move together with the second transmission worm in a direction parallel to the axial direction of the first transmission worm.

[0012] Optionally, the continuously variable transmission (CVT) further includes: The first reduction gear is disposed at the drive end of the first drive structure; The second reduction gear meshes with the first reduction gear for transmission, and the second reduction gear is coaxially located at the end of the first transmission worm that is away from the shifting mechanism. The fifth transmission bevel gear is coaxially mounted on the first transmission worm gear; The sixth transmission bevel gear meshes with the fifth transmission bevel gear, and the sixth transmission bevel gear is coaxially mounted on the first output shaft.

[0013] Optionally, in the above-mentioned continuously variable transmission (CVT) gear shifting device, a first worm wheel is coaxially arranged on the second transmission worm, and the first worm wheel meshes with the worm portion on the first transmission worm for transmission. The second drive structure is used to drive the first worm wheel to the meshing position on the first transmission worm.

[0014] Optionally, in the above-mentioned continuously variable transmission (CVT) gear shifting device, the housing is provided with multiple rotating bearing components, which are used to correspondingly support the first drive structure, the first transmission worm, the first output shaft, the second transmission worm, the first transmission shaft, and the second output shaft.

[0015] Compared with the prior art, when the above technical solution is adopted, the first drive structure is activated, and the drive end of the first drive structure drives the first transmission worm to rotate continuously. Through the meshing of the first transmission worm with the gear of the first output shaft, the first output shaft is driven to rotate around its own axis. The rotation of the first output shaft provides stable rotational power for the upper roll. At the same time, the first transmission worm and the second transmission worm mesh and drive the second transmission worm to rotate around its own axis. During the rotation of the second transmission worm, the meshing transmission is completed through the first shift bevel gear on the first transmission shaft, driving the first transmission shaft to rotate. Then, through the first transmission bevel gear on the first transmission shaft and the second transmission bevel gear on the second output shaft, the first transmission bevel gear on the first transmission shaft meshes and drives the first transmission shaft to rotate. The meshing transmission between the gears enables the second output shaft to rotate, providing stable rotational power to the lower roll. When it is necessary to adjust the speed of the second output shaft, the second drive structure is activated, causing it to drive the second transmission worm to translate in a direction parallel to the axial direction of the first transmission worm. This adjusts the meshing position where the second and first transmission worms intersect. During the translation, the meshing position between the worm portion of the second transmission worm and the first shift bevel gear on the first transmission shaft changes. Through the meshing of the first transmission bevel gear on the first transmission shaft and the second transmission bevel gear on the second output shaft, the first transmission shaft drives the second output shaft to rotate in the opposite direction. The movement path of the bevel gear at the meshing position has an inclination angle with the axial direction of the first transmission shaft. When the second transmission worm moves axially, the meshing point of the first transmission bevel gear and the worm part of the second transmission worm continuously shifts along the conical surface of the first transmission bevel gear. The effective transmission radius at the meshing point continuously changes, and the transmission ratio is smoothly adjustable, realizing stepless adjustment of the second output shaft speed. Compared with the asynchronous rolling mill that uses a mechanical graded speed change mechanism, this application, through the integrated structural design of double worm cross meshing transmission, bevel gear reversing transmission, and shifting mechanism, relies on the housing to provide a rotational support structure, ensuring the coaxiality and stability of all transmission components, reducing transmission clearance and movement. The system effectively prevents vibration and blocks external metal impurities, dust, and other foreign objects from entering the gaps between the gear meshing parts, ensuring the stability of the transmission structure. This allows the first and second output shafts to provide stable speeds during operation, extending the service life of the shifting device. Furthermore, the second drive structure can quickly switch gears by adjusting the meshing position of the second transmission worm, flexibly adapting to different rolling conditions. It can stably achieve reverse synchronous operation and speed ratio adjustment of the upper and lower rolls without the need for additional reversing components, and can adjust the speed of the upper and lower rolls without stopping the mill, ensuring real-time and continuous shifting during rolling and thus improving rolling efficiency.

[0016] Secondly, the present invention also provides an asynchronous rolling mill, comprising: a frame, an upper roll, a lower roll, and a continuously variable speed ratio shifting device as described above. The upper roll and the lower roll are rotatably mounted on the frame, and the upper roll and the lower roll are arranged alternately from top to bottom. The axial direction of the upper roll is parallel to the axial direction of the lower roll. The upper roll is drivenly connected to a first output shaft, and the lower roll is drivenly connected to a second output shaft.

[0017] Compared with the prior art, when adopting the above technical solution, the first drive structure is activated, causing the first output shaft and the second output shaft to rotate. The upper roll connected to the first output shaft and the lower roll connected to the second output shaft begin to rotate relative to each other. The plate is placed in the gap between the upper and lower rolls. During the continuous rotation of the upper and lower rolls, rolling force is generated on the plate. Due to the load introduced between the upper and lower rolls, the speed provided by the asynchronous mill is unstable. The operator can use the second drive structure to drive the second transmission worm to translate along the axial direction of the first transmission worm, thereby completing the real-time adjustment of the speed of the second output shaft. There is no need to stop the asynchronous mill to change gears. The operator can change the speed of the second output shaft in real time according to the deformation state of the rolled material, so that the first output shaft 4 and the second output shaft 7 can provide a stable speed, and achieve a continuous and stable speed ratio between the upper and lower rolls. Compared with the traditional asynchronous mill that frequently stops to change gears and disrupts the continuity of production, this application achieves the stability and continuity of speed ratio adjustment during the operation of the asynchronous mill through the integrated structural design of the gear changing mechanism and the transmission meshing structure. Attached Figure Description

[0018] The accompanying drawings, which are included to provide a further understanding of the invention and form part of this invention, illustrate exemplary embodiments of the invention and are used to explain the invention, but do not constitute an undue limitation of the invention. In the drawings: Figure 1 This is a schematic diagram of the overall structure of a continuously variable speed ratio shifting device and an asynchronous rolling mill provided in an embodiment of the present invention; Figure 2 This is a schematic diagram of a continuously variable transmission (CVT) gear shifting device provided in an embodiment of the present invention; Figure 3 for Figure 2 A schematic diagram of the internal structure; Figure 4 for Figure 3 Schematic diagram of the upper and middle roll drive system; Figure 5 for Figure 3 Schematic diagram of the structure of the middle and lower roll drive system; Figure 6 This is a schematic diagram showing the direction of rotation of the first output shaft in a continuously variable transmission (CVT) device provided in an embodiment of the present invention. Figure 7This is a schematic diagram showing the direction of rotation of the second output shaft in a continuously variable transmission (CVT) device provided in an embodiment of the present invention. Figure 8 This is a schematic diagram of the small-end speed ratio transmission state of the first shifting bevel gear in a continuously variable transmission device provided in an embodiment of the present invention; Figure 9 This is a structural schematic diagram of the large-end speed ratio transmission state of the first shifting bevel gear in a continuously variable transmission device provided in an embodiment of the present invention.

[0019] Figure label: 1-Box housing; 11-Rotating bearing component; 2-First drive structure; 21-First reduction gear; 3-First transmission worm; 31-Second reduction gear; 32-Fifth transmission bevel gear; 4-First output shaft; 41-Sixth transmission bevel gear; 5-Shifting mechanism; 51-Second transmission worm; 52-Second drive structure; 521-Telescopic rod; 522-Drive component; 53-First worm wheel; 6-First transmission shaft; 61-First shifting bevel gear; 62-First transmission bevel gear; 7-Second output shaft; 71-Second transmission bevel gear; 72-Fourth transmission bevel gear; 81-Upper roll; 82-Lower roll; 83-Frame; 9-Second transmission shaft; 91-Second shifting bevel gear; 92-Third transmission bevel gear. Detailed Implementation

[0020] To make the technical problems to be solved, the technical solutions, and the beneficial effects of the present invention clearer, the present invention 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 invention and are not intended to limit the present invention.

[0021] It should be noted that when a component is referred to as being "fixed to" or "set on" another component, it can be directly on or indirectly on that other component. When a component is referred to as being "connected to" another component, it can be directly connected to or indirectly connected to that other component.

[0022] Furthermore, 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 invention, "a plurality of" means two or more, unless otherwise explicitly specified. "Several" means one or more, unless otherwise explicitly specified.

[0023] In the description of this invention, it should be understood that the terms "upper", "lower", "front", "rear", "left", "right", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this invention 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. Therefore, they should not be construed as limitations on this invention.

[0024] In the description of this invention, it should be noted that, unless otherwise explicitly specified and limited, the terms "installation," "connection," and "linking" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components. Those skilled in the art can understand the specific meaning of the above terms in this invention according to the specific circumstances.

[0025] like Figures 1-9 As shown in the figure, an embodiment of the present invention provides a continuously variable transmission (CVT) gear shifting device, hereinafter referred to as the shifting device. It includes: a housing 1, a first drive structure 2, a first transmission worm gear 3, a first output shaft 4, a shifting mechanism 5, a first transmission shaft 6, and a second output shaft 7.

[0026] The first drive structure 2 has its drive end rotatably supported on the housing 1; the first transmission worm 3 is connected to the drive end of the first drive structure 2, and is rotatably supported on the housing 1, with the first drive structure 2 driving the first transmission worm 3 to rotate; the first output shaft 4 is gear-engaged with the first transmission worm 3, and is rotatably supported on the housing 1, with the first output shaft 4 being connected to the upper roller 81; the shifting mechanism 5 has a second transmission worm 51 and a second drive structure 52, the second transmission worm 51 is gear-engaged with the first transmission worm 3, and the rotation axis of the first transmission worm 3 intersects with the rotation axis of the second transmission worm 51, with the drive end of the second drive structure 52 connected to the second transmission worm 51. One end of 1 is connected to the second drive structure 52, which is used to drive the second transmission worm 51 to move in a direction parallel to the axial direction of the first transmission worm 3; the first transmission shaft 6 is rotatably supported on the housing 1, and the first shift bevel gear 61 and the first transmission bevel gear 62 are coaxially arranged on the first transmission shaft 6. The first shift bevel gear 61 meshes with the worm part on the second transmission worm 51 for transmission; the second transmission bevel gear 71 on the second output shaft 7 meshes with the first transmission bevel gear 62 for transmission. The second output shaft 7 is rotatably supported on the housing 1, and the rotation direction of the second output shaft 7 is opposite to the rotation direction of the first output shaft 4. The axial direction of the first output shaft 4 is parallel to the axial direction of the second output shaft 7. The second output shaft 7 is used for transmission connection with the lower roller 82.

[0027] In specific implementation, such as Figure 3 As shown, the first drive structure 2 is activated, and the drive end of the first drive structure 2 drives the first transmission worm 3 to rotate continuously. Through the meshing of the first transmission worm 3 with the gear of the first output shaft 4, the first output shaft 4 is driven to rotate around its own axis. The rotation of the first output shaft 4 provides stable rotational power for the upper roll 81. At the same time, the first transmission worm 3 and the second transmission worm 51 mesh and drive the second transmission worm 51 to rotate around its own axis. During the rotation of the second transmission worm 51, the meshing transmission is completed through the first shifting bevel gear 61 on the first transmission shaft 6, driving the first transmission shaft 6 to rotate. Then, through the meshing between the first transmission bevel gear 62 on the first transmission shaft 6 and the second transmission bevel gear 71 on the second output shaft 7, the first transmission worm 51 completes the meshing transmission. The transmission causes the second output shaft 7 to rotate, providing stable rotational power to the lower roll 82. When it is necessary to adjust the speed of the second output shaft 7, the second drive structure 52 is activated, causing the second drive structure 52 to drive the second transmission worm 51 to translate in a direction parallel to the axial direction of the first transmission worm 3. This adjusts the meshing position between the second transmission worm 51 and the first transmission worm 3. During the translation, the meshing position between the worm portion of the second transmission worm 51 and the first shift bevel gear 61 on the first drive shaft 6 changes. Through the meshing engagement between the first transmission bevel gear 62 on the first drive shaft 6 and the second transmission bevel gear 71 on the second output shaft 7, the first drive shaft 6 drives the second output shaft 7 to rotate in the opposite direction. Because the movement path of the meshing position of the first shift bevel gear 61 has an inclination angle with the axial direction of the first transmission shaft 6, when the second transmission worm 51 translates axially, the meshing point of the first transmission bevel gear 62 and the worm portion of the second transmission worm 51 continuously shifts along the conical surface of the first transmission bevel gear 62. The effective transmission radius at the meshing point continuously changes, and the transmission ratio is smoothly adjustable, realizing stepless adjustment of the speed of the second output shaft 7. Compared with the asynchronous rolling mill that uses a mechanical graded speed change mechanism in the traditional way, this application, through the integrated structural design of double worm cross meshing transmission, bevel gear reversing transmission and shifting mechanism 5, relies on the housing 1 to provide a rotational support structure, ensuring the coaxiality and stability of the operation of all transmission components and reducing transmission clearance. This design prevents vibrations during operation and blocks external metal impurities, dust, and other foreign objects from entering the gaps between the gear meshing parts, ensuring the stability of the transmission structure. This allows the first output shaft 4 and the second output shaft 7 to provide stable speeds during operation, extending the service life of the shifting device. Furthermore, the second drive structure 52 can quickly switch transmission gears by adjusting the meshing position of the second transmission worm 51, flexibly adapting to different rolling conditions. It can stably achieve reverse synchronous operation and speed ratio adjustment of the upper roll 81 and the lower roll 82 without the need for additional reversing components, and can adjust the speed of the upper roll 81 and the lower roll 82 without stopping the rolling mill, ensuring the real-time and continuous shifting during rolling and thus improving rolling efficiency.

[0028] In some embodiments, the ratio of the rotational speed of the first output shaft 4 to the rotational speed of the second output shaft 7 is 0.7 to 1.3. For example, the ratio of the rotational speed of the first output shaft 4 to the rotational speed of the second output shaft 7 can be 0.7, 0.8, 0.85, 0.9, 1, 1.1, 1.05, 1.2, 1.25, 1.3, etc. With this setting, operators can match the ratio according to different rolling process requirements. By adjusting the rotational speeds of the first output shaft 4 and the second output shaft 7, the sliding friction loss between the upper roll 81, the lower roll 82 and the sheet metal can be reduced, wear on the upper roll 81 and the lower roll 82 can be reduced, and the service life of the upper roll 81 and the lower roll 82 can be extended.

[0029] like Figure 5 , Figure 7 and Figure 8 As shown, in some embodiments, the continuously variable transmission (CVT) gear shifting device further includes a second drive shaft 9, which is rotatably supported on the housing 1. The second drive shaft 9 and the first drive shaft 6 are axially symmetrically distributed relative to the second transmission worm 51. A second shift bevel gear 91 and a third transmission bevel gear 92 are coaxially arranged on the second drive shaft 9. The second shift bevel gear 91 meshes with the worm portion on the second transmission worm 51, and the third transmission bevel gear 92 meshes with the fourth transmission bevel gear 72 on the second output shaft 7.

[0030] During operation, the second drive structure 52 drives the second transmission worm 51 to translate along its own axial direction. Simultaneously, the worm portion of the second transmission worm 51 meshes with the first shift bevel gear 61 and the second shift bevel gear 91, which are symmetrically arranged along its axial direction. During the translation, the meshing point shifts synchronously along the inclined conical surfaces of the two sets of bevel gears, thus changing the effective transmission radius at the meshing point. The first shift bevel gear 61 rotates synchronously with the first drive shaft 6, transmitting power through the meshing of the first transmission bevel gear 62 with the second transmission bevel gear 71 on the second output shaft 7. The second shift bevel gear 91 rotates synchronously with the second drive shaft 9, then synchronously outputs power to the second output shaft 7 through the meshing of the third transmission bevel gear 92 with the fourth transmission bevel gear 72. This configuration, through the symmetrical arrangement of the first drive shaft 6 and the second drive shaft 9, synchronously cancels the axial force generated by the worm gear meshing, ensuring the smoothness and reliability of the shifting adjustment process.

[0031] like Figure 7 and Figure 8As shown, in some embodiments, the first shift bevel gear 61 and the second shift bevel gear 91 have the same structure, and the bevel angle of the first shift bevel gear 61 is 45°~60°. For example, the bevel angle of the first shift bevel gear 61 can be 45°, 48°, 50°, 52°, 55°, 57°, 60°, etc. This configuration ensures that the first shift bevel gear 61 and the second shift bevel gear 91 have identical structures, facilitating the processing, repair, and replacement of parts, reducing the types of mold processing, and lowering equipment production, assembly, and subsequent maintenance costs. Furthermore, a bevel angle greater than 45° can increase the root thickness of the first shift bevel gear 61 and the second shift bevel gear 91, improving their bending and impact resistance. To enhance load-bearing capacity and prevent tooth breakage and root cracking under heavy-load rolling conditions, the bevel tooth angle is less than 60°. During the axial translation of the second transmission worm 51, the meshing points between the second transmission worm 51 and the first shift bevel gear 61 and the second shift bevel gear 91 can smoothly and continuously slide along the bevel tooth slope, improving the range of transmission radius variation, reasonably distributing the axial force generated by meshing, reducing the sliding friction loss between the tooth surfaces of the second transmission worm 51 and the first shift bevel gear 61 and the second shift bevel gear 91, and improving the stability and service life of the shifting device.

[0032] like Figure 7 and Figure 8 As shown, in some embodiments, the small end of the first shift bevel gear 61 and the small end of the second shift bevel gear 91 both face the second transmission worm 51, while the large end of the first shift bevel gear 61 and the large end of the second shift bevel gear 91 both face the second output shaft 7. With this configuration, when the second transmission worm 51 moves axially to adjust its speed, the meshing point of the second transmission worm 51 on the first shift bevel gear 61 continuously transitions from the small end to the large end. Since the number of teeth Z2 at the large end of the first shift bevel gear 61 is greater than the number of teeth Z1 at the small end, the effective transmission radius of the meshing changes smoothly from small to large. The number of meshing teeth between the second transmission worm 51 and the first shift bevel gear 61, and between the second transmission worm 51 and the second shift bevel gear 91, changes, causing the rotational speed of the second output shaft 7 to increase from low speed to high speed. The high-speed continuous stepless adjustment is achieved by having the large ends of the first shift bevel gear 61 and the second shift bevel gear 91 close to the speed output side of the first transmission shaft 6. The large ends of the first shift bevel gear 61 and the second shift bevel gear 91 have larger tooth thickness and higher load-bearing strength, which can withstand the high torque output load under rolling conditions and reduce the problems of tooth root fracture and excessive tooth surface wear. The two sets of bevel gears are symmetrically assembled in the same direction, which further reduces the running axial movement of the second transmission worm 51 and ensures the stability and reliability of the shift mechanism 5 under frequent speed adjustment conditions.

[0033] In other embodiments, the small end of the first shift bevel gear 61 and the small end of the second shift bevel gear 91 both face the second output shaft 7, while the large end of the first shift bevel gear 61 and the large end of the second shift bevel gear 91 both face the second transmission worm 51. With this configuration, when the second transmission worm 51 moves axially to adjust its speed, the meshing point of the second transmission worm 51 on the first shift bevel gear 61 continuously transitions from the large end to the small end. Since the number of teeth Z2 at the large end of the first shift bevel gear 61 is greater than the number of teeth Z1 at the small end, the effective transmission radius of the meshing changes smoothly from large to small. This changes the number of meshing teeth between the second transmission worm 51 and the first shift bevel gear 61, as well as between the second transmission worm 51 and the second shift bevel gear 91, causing the rotational speed of the second output shaft 7 to continuously decrease from high speed to low speed. The stepless adjustment is achieved by having the large ends of the first shift bevel gear 61 and the second shift bevel gear 91 close to the rotation input side of the second transmission worm 51. The wide tooth surfaces of the large ends of the first shift bevel gear 61 and the second shift bevel gear 91 fully mesh with the second transmission worm 51, which can disperse the meshing pressure, reduce pitting and wear on the tooth surfaces, and adapt to high torque input conditions. The two sets of bevel gears are symmetrically and in the same direction, which further reduces the axial movement of the second transmission worm 51 and ensures the stability and reliability of the shift mechanism 5 under frequent speed adjustment conditions.

[0034] In some embodiments, the second drive structure 52 includes a telescopic rod 521 and a drive member 522. The telescopic rod 521 is fixedly connected to one end of the second transmission worm 51, and the telescopic direction of the telescopic rod 521 is parallel to the axial direction of the first transmission worm 3. The drive member 522 is connected to the telescopic rod 521 and is used to drive the telescopic rod 521 to move together with the second transmission worm 51 in a direction parallel to the axial direction of the first transmission worm 3. With this configuration, the drive member 522 drives the telescopic rod 521 to move, and the telescopic direction of the telescopic rod 521 is parallel to the axial direction of the first transmission worm 3. The output power of the drive member 522 can directly drive the second transmission worm 51 to perform synchronous axial translation. The telescopic rod 521 can stably constrain the motion posture of the second transmission worm 51 during the translation process, preventing the second transmission worm 51 from radially deviating or wobbling, so that the second transmission worm 51 and the first shift bevel gear 61 and the second shift bevel gear 91 on both sides always maintain good meshing, reducing the eccentric wear of the tooth surface. The drive component 522 can be provided in one or two ways. When there are two drive components 522, they are respectively located at both ends of the telescopic rod 521. The two drive components 522 can operate synchronously, further improving the transmission efficiency of the second transmission worm 51 moving in a direction parallel to the axis of the first transmission worm 3. When one drive component 522 fails, the shifting device does not need to stop; it only needs to start the other drive component 522 to continue the shifting action. This improves the continuity of shifting during rolling, reduces the downtime of the production line due to drive component failure, and further improves the production efficiency of rolling. Specifically, the drive component 522 includes a pneumatic cylinder, a hydraulic cylinder, or an electric cylinder. Of course, the drive component 522 can also use other linear drive components, as long as it can stably drive the telescopic rod 521 and the second transmission worm 51 to complete the axial translational movement of the first transmission worm 3.

[0035] In some embodiments, the continuously variable transmission (CVT) gear shifting device further includes: a first reduction gear 21, a second reduction gear 31, a fifth transmission bevel gear 32, and a sixth transmission bevel gear 41. The first reduction gear 21 is disposed at the drive end of the first drive structure 2; the second reduction gear 31 meshes with the first reduction gear 21 and is coaxially disposed at the end of the first transmission worm gear 3 away from the shifting mechanism 5; the fifth transmission bevel gear 32 is coaxially disposed on the first transmission worm gear 3; the sixth transmission bevel gear 41 meshes with the fifth transmission bevel gear 32 and is coaxially disposed on the first output shaft 4. With this configuration, the output end of the first drive structure 2 is connected to the first reduction gear 21 and the second reduction gear 31 in sequence to form a first-stage reduction transmission pair, which transmits power to the first transmission worm 3 coaxially fixed to the second reduction gear 31. This reduces the output speed of the first drive structure 2 and amplifies the output torque, meeting the high torque requirements of the upper roll 81 rolling operation. The multiple gear meshing transmissions make the shifting device have a strong load-bearing capacity and a stable transmission ratio, which can reduce the speed fluctuation of the first output shaft 4 and the second output shaft 7 during the transmission process and extend the service life of the shifting device.

[0036] like Figure 3 and Figure 6 As shown, in some embodiments, a first worm wheel 53 is coaxially disposed on the second transmission worm 51, and the first worm wheel 53 meshes with the worm portion on the first transmission worm 3 for transmission. The second drive structure 52 is used to drive the first worm wheel 53 to the meshing position on the first transmission worm 3. With this configuration, the first worm wheel 53, coaxially mounted with the second transmission worm 51, forms a worm-worm wheel meshing pair with the worm portion of the first transmission worm 3. Relying on the self-locking and stable transmission ratio characteristics of the worm-worm wheel transmission, rotational power can be stably obtained from the first transmission worm 3 and transmitted to the second transmission worm 51, ensuring the continuity and reliability of power input on the speed adjustment and shifting branch. The second drive structure 52 drives the second transmission worm 51 and the first worm wheel 53 to move axially synchronously, changing the axial meshing position of the first worm wheel 53 and the first transmission worm 3. The structure is simple, and the worm-worm wheel meshing contact tooth surface has many surfaces, strong load-bearing capacity, low transmission noise, and good buffering and vibration reduction effect. It can adapt to the heavy-load transmission requirements of rolling equipment, reduce the radial runout problem of transmission components, and complete the continuous and smooth adjustment of the speed ratio of the second output shaft 7, further reducing the vibration loss of the shifting device during high-speed rolling.

[0037] In some embodiments, the housing 1 is provided with multiple rotating bearing components 11, which are used to correspondingly rotate and support the first drive structure 2, the first transmission worm 3, the first output shaft 4, the second transmission worm 51, the first transmission shaft 6, and the second output shaft 7. With this configuration, multiple independently arranged rotating bearing components 11 are mounted on the housing 1. Each rotating bearing component 11 provides fixed-point rotational support to the first drive structure 2, the first transmission worm 3, the first output shaft 4, the second transmission worm 51, the first transmission shaft 6, and the second output shaft 7, further controlling the meshing clearance of the transmission pairs and avoiding the risk of swaying or slippage during shaft operation, thus ensuring the meshing alignment accuracy between the various structures. Specifically, the rotating bearing components 11 can be sliding bearings or rolling bearings, and the operator can flexibly select them according to the shaft load and speed conditions. Of course, other rotating support components can also be used for the rotating bearing components 11, as long as the rotating bearing components can reliably limit the radial and axial movement of each shaft, and are not limited to the structural forms listed in this embodiment.

[0038] Meanwhile, the present invention also provides an asynchronous rolling mill, including: a frame 83, an upper roll 81, a lower roll 82, and a stepless speed ratio shifting device as described in any of the above embodiments. The upper roll 81 and the lower roll 82 are rotatably mounted on the frame 83. The upper roll 81 and the lower roll 82 are arranged alternately from top to bottom. The axial direction of the upper roll 81 is parallel to the axial direction of the lower roll 82. The upper roll 81 is drivenly connected to the first output shaft 4, and the lower roll 82 is drivenly connected to the second output shaft 7.

[0039] In specific implementation, such as Figure 1 As shown, activating the first drive structure 2 causes the first output shaft 4 and the second output shaft 7 to rotate. The upper roll 81 connected to the first output shaft 4 and the lower roll 82 connected to the second output shaft 7 begin to rotate relative to each other. A sheet material is placed in the gap between the upper roll 81 and the lower roll 82. As the upper roll 81 and the lower roll 82 rotate continuously, a rolling force is generated on the sheet material. Due to the load introduced between the upper and lower rolls 82, the speed provided by the asynchronous mill is unstable. The operator can drive the second transmission worm 51 along the axis of the first transmission worm 3 through the second drive structure 52. The translational motion enables real-time adjustment of the rotational speed of the second output shaft 7, eliminating the need for the asynchronous rolling mill to stop and change gears. Operators can change the rotational speed of the second output shaft 7 in real time according to the deformation state of the rolled material, so that the first output shaft 4 and the second output shaft 7 can provide stable rotational speeds. This achieves a continuous and stable speed ratio between the upper roll 81 and the lower roll 82. Compared with traditional asynchronous rolling mills that frequently stop and change gears, disrupting production continuity, this application achieves the stability and continuity of speed ratio adjustment during the operation of the asynchronous rolling mill through the integrated structural design of the gear-changing mechanism 5 and the transmission meshing structure.

[0040] In the description of the above embodiments, specific features, structures, materials, or characteristics may be combined in any suitable manner in one or more embodiments or examples.

[0041] The above description is merely a specific embodiment of the present invention, but the scope of protection of the present invention is not limited thereto. Any variations or substitutions that can be easily conceived by those skilled in the art within the technical scope disclosed in the present invention should be included within the scope of protection of the present invention. Therefore, the scope of protection of the present invention should be determined by the scope of the claims.

Claims

1. A continuously variable transmission (CVT) gear shifting device, characterized in that, include: Box; A first driving structure, wherein the driving end of the first driving structure is rotatably supported by the housing; The first transmission worm gear is connected to the drive end of the first drive structure. The first transmission worm gear is rotatably supported on the housing. The first drive structure is used to drive the first transmission worm gear to rotate. The first output shaft meshes with the first transmission worm gear for transmission, the first output shaft is rotatably supported on the housing, and the first output shaft is used to connect with the upper roller transmission; The shifting mechanism has a second transmission worm and a second drive structure. The second transmission worm meshes with the first transmission worm gear, and the rotation axis of the first transmission worm intersects with the rotation axis of the second transmission worm. The drive end of the second drive structure is connected to one end of the second transmission worm. The second drive structure is used to drive the second transmission worm to move in a direction parallel to the axis of the first transmission worm. A first drive shaft is rotatably supported on the housing, and a first shift bevel gear and a first transmission bevel gear are coaxially arranged on the first drive shaft. The first shift bevel gear meshes with the worm portion on the second transmission worm for transmission. The second output shaft has a second transmission bevel gear that meshes with the first transmission bevel gear. The second output shaft is rotatably supported by the housing, and the rotation direction of the second output shaft is opposite to that of the first output shaft. The axial direction of the first output shaft is parallel to that of the second output shaft. The second output shaft is used for transmission connection with the lower roll.

2. The continuously variable transmission (CVT) gear shifting device according to claim 1, characterized in that, The ratio of the rotational speed of the first output shaft to the rotational speed of the second output shaft is 0.7 to 1.

3.

3. The continuously variable transmission (CVT) gear shifting device according to claim 1, characterized in that, Also includes: The second drive shaft is rotatably supported on the housing. The second drive shaft and the first drive shaft are symmetrically distributed axially relative to the second drive worm. A second shift bevel gear and a third drive bevel gear are coaxially arranged on the second drive shaft. The second shift bevel gear meshes with the worm portion on the second drive worm, and the third drive bevel gear meshes with a fourth drive bevel gear on the second output shaft.

4. The continuously variable transmission (CVT) gear shifting device according to claim 3, characterized in that, The first shift bevel gear and the second shift bevel gear have the same structure, and the bevel angle of the first shift bevel gear is 45°~60°.

5. The continuously variable transmission (CVT) gear shifting device according to claim 3, characterized in that, The small ends of the first shift bevel gear and the second shift bevel gear both face the second transmission worm, and the large ends of the first shift bevel gear and the second shift bevel gear both face the second output shaft; Alternatively, the small ends of the first shift bevel gear and the second shift bevel gear both face the second output shaft, and the large ends of the first shift bevel gear and the second shift bevel gear both face the second transmission worm.

6. The continuously variable transmission (CVT) gear shifting device according to claim 1, characterized in that, The second driving structure includes: A telescopic rod is fixedly connected to one end of the second transmission worm gear, and the telescopic direction of the telescopic rod is parallel to the axial direction of the first transmission worm gear; A driving component, connected to the telescopic rod, is used to drive the telescopic rod to move together with the second transmission worm gear in a direction parallel to the axial direction of the first transmission worm gear.

7. The continuously variable transmission (CVT) gear shifting device according to claim 1, characterized in that, Also includes: The first reduction gear is disposed at the drive end of the first drive structure; The second reduction gear meshes with the first reduction gear for transmission, and the second reduction gear is coaxially disposed at the end of the first transmission worm gear away from the shifting mechanism; The fifth transmission bevel gear is coaxially mounted on the first transmission worm gear; The sixth transmission bevel gear meshes with the fifth transmission bevel gear, and the sixth transmission bevel gear is coaxially disposed on the first output shaft.

8. The continuously variable transmission (CVT) gear shifting device according to claim 1, characterized in that, A first worm wheel is coaxially arranged on the second transmission worm, and the first worm wheel meshes with the worm portion on the first transmission worm for transmission. The second driving structure is used to drive the first worm wheel to the meshing position on the first transmission worm.

9. The continuously variable transmission (CVT) gear shifting device according to claim 1, characterized in that, The housing is provided with multiple rotating bearing components, which are used to rotatably support the first drive structure, the first transmission worm, the first output shaft, the second transmission worm, the first transmission shaft, and the second output shaft.

10. An asynchronous rolling mill, characterized in that, include: The machine includes a frame, an upper roll, a lower roll, and a continuously variable speed ratio shifting device as described in any one of claims 1-9, wherein the upper roll and the lower roll are rotatably mounted on the frame, the upper roll and the lower roll are arranged alternately from top to bottom, the axial direction of the upper roll is parallel to the axial direction of the lower roll, the upper roll is drivenly connected to the first output shaft, and the lower roll is drivenly connected to the second output shaft.

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