Speed reducer of high-speed-ratio variable-speed oxygen lance elevator
By employing a dual-input-single-output-shaft design and a planetary gear assembly, the problems of insufficient load-bearing capacity and complex structure of the oxygen lance elevator reducer are solved, achieving efficient speed change and low-cost multi-stage transmission, which is suitable for large converter equipment.
Patent Information
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- JIANGSU GUOMAO REDUCER GRP CO LTD
- Filing Date
- 2025-08-12
- Publication Date
- 2026-05-19
AI Technical Summary
Existing oxygen lance elevator reducers suffer from problems such as insufficient load-bearing capacity, low speed-changing accuracy, complex structure, large size, heavy weight, and high cost. They are particularly difficult to meet the process requirements of high load and complex working conditions in large converter equipment.
It adopts a dual-input shaft and single-output shaft design, combined with multi-stage planetary gear transmission. By assembling the planetary gear assembly with the main drive shaft, it achieves two output speeds with significant differences, optimizes the internal parts layout, reduces the number of shafts and gears, and shrinks the size and weight.
It achieves efficient multi-stage speed change, reduces costs, is applicable to more scenarios, meets the adjustment needs of different working conditions, and improves transmission efficiency and torque output.
Smart Images
Figure CN224260836U_ABST
Abstract
Description
Technical Field
[0001] This utility model relates to the field of speed reducer technology, and in particular to a speed reducer for a high-ratio variable-speed oxygen lance elevator. Background Technology
[0002] Early oxygen lance elevators used traditional reduction gears, which had problems such as insufficient load-bearing capacity and low speed change accuracy. With the development of converters to larger scales, such as those with a capacity of 100 tons or more, the equipment needs to cope with larger loads and more complex working conditions. The reducer needs to switch the high-speed, low-torque output of the motor to low-speed, high-torque output to match the process requirements of precise lifting and lowering of the oxygen lance.
[0003] Currently, traditional variable-speed oxygen lance hoist reducers typically employ a dual-input shaft and dual-output shaft transmission structure. The two speed ratio structures operate independently without interference. However, this results in a large number of internal structural parts, leading to a large overall size and weight, thus limiting application scenarios. This is especially problematic when the speed ratios differ significantly—for example, a lower ratio of around 50 and a higher ratio of over 700. In such cases, two separate reducers are usually used to achieve the speed change, but this is very costly. If both speed ratios are housed within the same reducer, the transmission efficiency of a fixed-shaft gear under varying load conditions is low, requiring more gears and shafts to accommodate the large speed ratio difference. This results in a crowded internal component layout, a large overall size and weight, higher costs, and is unfavorable for use and handling in certain scenarios. Utility Model Content
[0004] The technical problem to be solved by this utility model is to overcome the shortcomings of the prior art and provide a high-ratio variable speed oxygen lance elevator reducer. It adopts a dual-input shaft and single-output shaft design, combined with multi-stage speed change of planetary gears, which can optimize the internal parts layout space, reduce the overall size and weight, and reduce costs.
[0005] To solve the above-mentioned technical problems, the technical solution of this utility model is as follows:
[0006] A high-ratio variable-speed oxygen lance elevator reducer includes a reducer housing and a first input gear shaft and a main drive shaft that are rotatably disposed in the reducer housing and arranged coaxially.
[0007] A planetary mounting plate is provided at the front of the main drive shaft, and a planetary gear assembly is mounted on the planetary mounting plate. The rear end of the first input gear shaft extends into the main drive shaft and meshes with the inner ring of the planetary gear assembly.
[0008] A first transmission gear shaft is engaged with one side of the main drive shaft, and an output shaft is engaged with the first transmission gear shaft next to it.
[0009] The reducer housing is also rotatably equipped with a second input gear shaft and a second transmission gear shaft. The second input gear shaft meshes with the second transmission gear shaft for transmission, and the second transmission gear shaft meshes with the outer ring of the planetary gear assembly for transmission.
[0010] When the second input gear shaft is locked, the rotation of the first input gear shaft can drive the planetary gear assembly to rotate, thereby driving the planetary mounting disk to rotate, and then driving the main drive shaft to rotate.
[0011] When the first input gear shaft is locked, the rotation of the second input gear shaft can drive the second transmission gear shaft to rotate and drive the planetary gear assembly to rotate, which in turn drives the planetary mounting disk to rotate, thereby driving the main drive shaft to rotate.
[0012] Furthermore, the planetary gear assembly includes a double-layered outer ring gear and three planetary gears meshing with the inner ring gears.
[0013] The planetary mounting disk has three detachable drive columns, and the three planetary gears are rotatably mounted on the three drive columns. When the three planetary gears mesh and roll in the inner ring of the double-layer gear ring, they can drive the planetary mounting disk to rotate through the drive columns.
[0014] The rear end of the first input gear shaft is meshed with the middle of three planetary gears, and the front part of the second transmission gear shaft meshes with the outer ring of the double-layer gear ring for transmission.
[0015] Furthermore, the planetary mounting disk also includes two discs formed on the front of the main drive shaft and arranged at intervals, and three connecting columns connecting the two discs;
[0016] The three drive columns are detachably mounted between the two discs.
[0017] Furthermore, all three planetary gears are mounted on the drive column via self-aligning roller bearings.
[0018] Furthermore, the double-layer gear ring is provided with gear ring seats at both ends, and the inner side of the gear ring seat is assembled to the outer side of the main drive shaft through a first deep groove ball bearing.
[0019] Furthermore, the rear end of the first input gear shaft has a sun gear, which meshes with the middle of three planetary gears.
[0020] Furthermore, the rear end of the first input gear shaft is assembled to the inner side of the main drive shaft via a second deep groove ball bearing.
[0021] Furthermore, a main gear is assembled at the rear of the main drive shaft, and a middle gear is assembled at the rear of the first drive gear shaft, the middle gear meshing with the main gear;
[0022] A large gear is mounted at the front of the output shaft, and the large gear meshes with the toothed section of the first transmission gear shaft.
[0023] Furthermore, a pinion is mounted at the rear of the second transmission gear shaft, the toothed section of the second input gear shaft meshes with the pinion, and the toothed section of the second transmission gear shaft meshes with the outer ring of the planetary gear assembly.
[0024] Furthermore, the front ends of the first input gear shaft and the output shaft extend out of the reducer housing, and the rear end of the second input gear shaft extends out of the reducer housing.
[0025] By adopting the above technical solution, this utility model has the following beneficial effects:
[0026] 1. This utility model integrates a dual-input shaft and a single-output shaft into a single housing, and combines the internal planetary gear assembly with the planetary mounting plate on the main drive shaft to achieve two outputs with significantly different speed ratios, meeting customer needs. Furthermore, the internal structure is compact, reducing the number of shafts and gears, optimizing the internal parts layout, and minimizing internal space occupation, thereby reducing the overall size and weight, saving on parts material costs, and making it suitable for more scenarios.
[0027] 2. This utility model uses a planetary gear assembly as an intermediate transmission mechanism to achieve multi-stage speed change. Compared with traditional gear shaft direct transmission, it has higher transmission efficiency, can obtain a larger speed ratio and torque output, and meets the adjustment requirements of different working conditions. Attached Figure Description
[0028] Figure 1 This is a front view of an embodiment of the present utility model;
[0029] Figure 2 for Figure 1 Schematic diagram of the cross-sectional structure of section AA;
[0030] Figure 3 for Figure 2 A magnified view of a portion of the central structure;
[0031] Figure 4 This is a partial structural assembly diagram of an embodiment of the present utility model;
[0032] Figure 5 for Figure 4 Cross-sectional schematic diagram of the middle structure;
[0033] Figure 6 This is a structural assembly diagram of the planetary gear assembly according to an embodiment of the present utility model;
[0034] Figure 7 This is a schematic diagram of the main drive shaft in an embodiment of the present invention;
[0035] The components include: 1. Gearbox housing; 2. First input gear shaft; 20. External gear; 21. Second deep groove ball bearing; 3. Planetary gear assembly; 30. Double-layer gear ring; 300. Gear ring seat; 31. Planetary gear; 32. Self-aligning roller bearing; 4. Main drive shaft; 40. Main gear; 41. Wheel disc; 42. Connecting column; 43. Drive column; 5. First transmission gear shaft; 50. Intermediate gear; 6. Output shaft; 60. Large gear; 7. First deep groove ball bearing; 8. Second input gear shaft; 9. Second transmission gear shaft; 90. Small gear. Detailed Implementation
[0036] To make the contents of this utility model easier to understand, the present utility model will be further described in detail below with reference to specific embodiments and accompanying drawings.
[0037] like Figure 1-7 As shown in this embodiment, a high-ratio variable-speed oxygen lance hoist reducer is provided, which mainly consists of a reducer housing 1, a first input gear shaft 2, a planetary gear assembly 3, a main drive shaft 4, a first transmission gear shaft 5, an output shaft 6, a second input gear shaft 8, and a second transmission gear shaft 9. Each shaft is rotatably mounted within the reducer housing 1 via bearings. The front ends of the first input gear shaft 2 and the output shaft 6 are... Figure 2 The lower end extends out of the reducer housing 1, and the rear end of the second input gear shaft 8 is... Figure 2 The upper part extends out of the reducer housing 1, and the first input gear shaft 2 and the main drive shaft 4 are coaxially assembled. The rear half of the first input gear shaft 2 extends into the main drive shaft 4, and the front part of the main drive shaft 4 is hollow.
[0038] To achieve two outputs with significantly different speed ratios, this embodiment features a planetary mounting disk at the front of the main drive shaft 4. A planetary gear assembly 3 is mounted on the planetary mounting disk. The rear end of the first input gear shaft 2 extends into the main drive shaft 4 and meshes with the inner ring of the planetary gear assembly 3. Simultaneously, a first transmission gear shaft 5 meshes with the left side of the main drive shaft 4, and an output shaft 6 meshes with the left side of the first transmission gear shaft 5. A second input gear shaft 8 meshes with a second transmission gear shaft 9, and the second transmission gear shaft 9 meshes with the outer ring of the planetary gear assembly 3. Thus, during operation, in the first scenario, the second input gear shaft 8 is locked. When the first input gear shaft 2 rotates, it drives the planetary gear assembly 3 to rotate, which in turn drives the planetary mounting disk to rotate, which in turn drives the main drive shaft 4 to rotate. The main drive shaft 4 drives the first transmission gear shaft 5 to rotate, and finally drives the output shaft 6 to output the first larger speed ratio. In the second scenario, the first input gear shaft 2 is locked. When the second input gear shaft 8 rotates, it drives the second transmission gear shaft 9 to rotate and drives the planetary gear assembly 3 to rotate, which in turn drives the planetary mounting disk to rotate, which in turn drives the main drive shaft 4 to rotate. The main drive shaft 4 drives the first transmission gear shaft 5 to rotate, and finally drives the output shaft 6 to output the second smaller speed ratio.
[0039] Specifically, the planetary gear assembly 3 in this embodiment includes a double-layered gear ring 30 on the outer ring and three planetary gears 31 meshing with the inner ring. The planetary mounting disk has three detachably mounted drive posts 43. The three planetary gears 31 are rotatably mounted on the three drive posts 43. When the three planetary gears 31 are engaged and rolling within the double-layered gear ring 30, they can drive the planetary mounting disk to rotate via the drive posts 43. Simultaneously, the rear end of the first input gear shaft 2 has a sun gear 20, which meshes with the three planetary gears 31. The toothed section at the front of the second transmission gear shaft 9 meshes with the outer ring of the double-layered gear ring 30 for transmission.
[0040] More specifically, the planetary mounting disk in this embodiment also includes two wheel disks 41 formed on the front of the main drive shaft 4 and arranged at intervals, and three connecting columns 42 connecting the two wheel disks 41. The main drive shaft 4, wheel disks 41, and connecting columns 42 are an integral structure, but the three drive columns 43 are detachably assembled between the two wheel disks 41 and fixed by screws and pins to facilitate the assembly of the planetary gears 31. In order to achieve normal rolling operation of the three planetary gears 31 in the inner ring of the double-layer gear ring 30, each planetary gear 31 is also assembled on the drive column 43 through a self-aligning roller bearing 32. This ensures the normal operation of the three planetary gears 31 and the smooth operation of the mechanism, and can drive the two wheel disks 41 to rotate through the intermediate drive column 43, thereby driving the main drive shaft 4 to rotate.
[0041] In the above design, this embodiment integrates a dual-input shaft and a single-output shaft into a single housing. Combined with the assembly design of the internal planetary gear assembly 3 and the planetary mounting plate on the main drive shaft 4, it can achieve two outputs with significantly different speed ratios to meet customer needs. Furthermore, the compact internal structure reduces the number of shafts and gears, optimizes the internal parts layout, and minimizes internal space occupation, thereby reducing the overall size and weight, saving on parts material costs, and making it suitable for more scenarios. Moreover, by using the planetary gear assembly 3 as an intermediate transmission mechanism, multi-stage speed changes can be achieved, resulting in higher transmission efficiency compared to traditional direct gear shaft transmission. This allows for larger speed ratios and torque outputs, meeting the adjustment requirements of different operating conditions.
[0042] To ensure the smooth operation of the planetary gear assembly 3, gear ring seats 300 are provided at both ends of the double-layer gear ring 30 in this embodiment. The inner side of the gear ring seat 300 is mounted on the outer side of the main drive shaft 4 through a first deep groove ball bearing 7. This not only ensures the smooth support of the planetary gear assembly 3 during operation, but also ensures that the two speed ratios do not affect each other and prevents interference between the double-layer gear ring 30 and the main drive shaft 4.
[0043] Furthermore, to ensure no interference between the first input gear shaft 2 and the main drive shaft 4, in this embodiment, the rear center of the first input gear shaft 2 extends into the main drive shaft 4. The main drive shaft 4 has an internal slot, and the extension of the first input gear shaft 2 is assembled with the internal slot of the main drive shaft 4 via a second deep groove ball bearing 21. This provides support for the first input gear shaft 2 and also prevents interference between the two shafts.
[0044] Of course, in order to achieve smooth transmission of the mechanism, a main gear 40 is assembled at the rear of the main drive shaft 4 in this embodiment, and a medium gear 50 is assembled at the rear of the first drive gear shaft 5. The medium gear 50 meshes with the main gear 40. A large gear 60 is assembled at the front of the output shaft 6. The large gear 60 meshes with the toothed section of the first drive gear shaft 5. When the second input gear shaft 8 is locked, the double-layer gear ring 30 is also locked. When the first input gear shaft 2 rotates, the sun gear 20 drives the three planetary gears 31 to roll inside the double-layer gear ring 30. This, in turn, drives the planetary mounting disk to rotate through the three drive columns 43, which in turn drives the main drive shaft 4 to rotate. The main gear 40 on the main drive shaft 4 drives the medium gear 50 to rotate, which in turn drives the first drive gear shaft 5 to rotate. The toothed section at the front of the first drive gear shaft 5 drives the large gear 60 to rotate, and finally drives the output shaft 6 to output the first larger speed ratio.
[0045] Meanwhile, in this embodiment, a small gear 90 is mounted at the rear of the second transmission gear shaft 9. The toothed section of the second input gear shaft 8 meshes with the small gear 90, and the toothed section of the second transmission gear shaft 9 meshes with the outer ring of the double-layer gear ring 30. When the first input gear shaft 2 is locked, the outer sun gear 20 is also locked. When the second input gear shaft 8 rotates, it drives the small gear 90 to rotate through the toothed section, which in turn drives the second transmission gear shaft 9 to rotate. This drives the double-layer gear ring 30 to rotate, which in turn drives the three planetary gears 31 to roll inside the double-layer gear ring 30. This, in turn, drives the planetary mounting disk to rotate through the three drive pinions 43, which in turn drives the main transmission shaft 4 to rotate. The main gear 40 on the main transmission shaft 4 drives the intermediate gear 50 to rotate, which in turn drives the first transmission gear shaft 5 to rotate. The toothed section at the front of the first transmission gear shaft 5 drives the large gear 60 to rotate, and finally drives the output shaft 6 to output a second, smaller speed ratio.
[0046] In the description of this specification, references to terms such as "an embodiment," "example," "specific example," etc., indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of the present invention. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples.
[0047] The above specific embodiments further illustrate the technical problems, technical solutions, and beneficial effects of this utility model. It should be understood that the above descriptions are merely specific embodiments of this utility model and are not intended to limit this utility model. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of this utility model should be included within the protection scope of this utility model.
Claims
1. A reducer for a high-ratio variable-speed oxygen lance hoist, characterized in that: It includes a reducer housing (1) and a first input gear shaft (2) and a main drive shaft (4) that are rotatably disposed in the reducer housing (1) and coaxially arranged. The main drive shaft (4) is provided with a planetary mounting plate at the front, and a planetary gear assembly (3) is mounted on the planetary mounting plate. The rear end of the first input gear shaft (2) extends into the main drive shaft (4) and meshes with the inner ring of the planetary gear assembly (3). The main drive shaft (4) is engaged with a first drive gear shaft (5) on one side, and an output shaft (6) is engaged with the first drive gear shaft (5) next to it. The reducer housing (1) is also rotatably equipped with a second input gear shaft (8) and a second transmission gear shaft (9). The second input gear shaft (8) meshes with the second transmission gear shaft (9) for transmission, and the second transmission gear shaft (9) meshes with the outer ring of the planetary gear assembly (3) for transmission. When the second input gear shaft (8) is locked, the first input gear shaft (2) can drive the planetary gear assembly (3) to rotate, thereby driving the planetary mounting disk to rotate and then driving the main drive shaft (4) to rotate. When the first input gear shaft (2) is locked, the second input gear shaft (8) can drive the second transmission gear shaft (9) to rotate and drive the planetary gear assembly (3) to operate, and then drive the planetary mounting disk to rotate, thereby driving the main transmission shaft (4) to rotate.
2. The high-ratio variable-speed oxygen lance elevator reducer according to claim 1, characterized in that: The planetary gear assembly (3) includes a double-layer gear ring (30) on the outer ring and three planetary gears (31) meshing with the inner ring. The planetary mounting disk has three detachable drive columns (43), and the three planetary gears (31) are rotatably mounted on the three drive columns (43). When the three planetary gears (31) mesh and roll in the inner ring of the double-layer gear ring (30), they can drive the planetary mounting disk to rotate through the drive columns (43). The rear end of the first input gear shaft (2) is meshed and assembled in the middle of the three planetary gears (31), and the front part of the second transmission gear shaft (9) meshes with the outer ring of the double-layer gear ring (30) for transmission.
3. The high-ratio variable-speed oxygen lance elevator reducer according to claim 2, characterized in that: The planetary mounting disk also includes two wheel disks (41) formed on the front of the main drive shaft (4) and spaced apart, and three connecting columns (42) connected between the two wheel disks (41). The three drive columns (43) are detachably mounted between the two discs (41).
4. The high-ratio variable-speed oxygen lance elevator reducer according to claim 2, characterized in that: All three planetary gears (31) are mounted on the drive column (43) via self-aligning roller bearings (32).
5. The high-ratio variable-speed oxygen lance elevator reducer according to claim 2, characterized in that: The double-layer gear ring (30) is provided with gear ring seats (300) at both ends. The inner side of the gear ring seat (300) is assembled on the outer side of the main drive shaft (4) through the first deep groove ball bearing (7).
6. The high-ratio variable-speed oxygen lance elevator reducer according to claim 2, characterized in that: The first input gear shaft (2) has a sun external tooth (20) at its rear end, which meshes with the middle of three planetary gears (31).
7. The high-ratio variable-speed oxygen lance elevator reducer according to claim 6, characterized in that: The rear end of the first input gear shaft (2) is assembled with the inner side of the main drive shaft (4) through the second deep groove ball bearing (21).
8. The high-ratio variable-speed oxygen lance elevator reducer according to claim 1, characterized in that: The main drive shaft (4) is equipped with a main gear (40) at the rear, and the first drive gear shaft (5) is equipped with a middle gear (50) at the rear, and the middle gear (50) meshes with the main gear (40); The output shaft (6) is equipped with a large gear (60) at the front, and the large gear (60) meshes with the toothed section of the first transmission gear shaft (5).
9. A high-ratio variable-speed oxygen lance elevator reducer according to claim 8, characterized in that: The rear part of the second transmission gear shaft (9) is equipped with a small gear (90), the toothed section of the second input gear shaft (8) meshes with the small gear (90), and the toothed section of the second transmission gear shaft (9) meshes with the outer ring of the planetary gear assembly (3).
10. A high-ratio variable-speed oxygen lance elevator reducer according to claim 1, characterized in that: The front ends of the first input gear shaft (2) and the output shaft (6) extend out of the reducer housing (1), and the rear end of the second input gear shaft (8) extends out of the reducer housing (1).