Helical gear axial positioning mechanism of vertical speed reducer

Abstract

The utility model relates to the technical field of speed reducer transmission, in particular to a helical gear axial positioning mechanism of a vertical speed reducer, which comprises a shell, an input shaft is rotatably mounted on one side in the shell, a first helical gear is mounted on the input shaft, the first helical gear is meshed with a second helical gear, and a positioning component is arranged on the input shaft. The positioning assembly is used for counteracting axial force generated when the first bevel gear rotates. Compared with the prior art, through self-locking matching of the conical lining and the conical surface of the bevel gear, axial displacement is effectively prevented, and the transmission precision is guaranteed; the opposite combined belleville springs are adopted, impact loads are buffered, continuous pre-tightening force is provided, gap changes are automatically compensated, and the service life is prolonged; the end cover is in threaded connection with the shell to realize pressing force adjustment, so that the axial clamping force is flexibly controlled to adapt to multiple working conditions; the thrust bearing is arranged to convert rotation of the end cover into stable axial pressure, friction loss is reduced, operation stability and reliability are improved, and rigidity and durability of the whole mechanism are improved.

Description

Technical Field

[0001] This utility model relates to the field of speed reducer transmission technology, and in particular to an axial positioning mechanism for a helical gear in a vertical speed reducer. Background Technology

[0002] Vertical gear reducers are widely used in industries such as metallurgy, chemical engineering, building materials, and machinery manufacturing. They are compact, offer smooth transmission, and are flexible in installation, making them particularly suitable for applications with limited vertical space. In practical applications, helical gears are widely used in gear reducers for power transmission due to their smooth meshing and high transmission efficiency. However, during helical gear transmission, the characteristics of the tooth structure often generate a certain axial force. This force acts on the input shaft, causing axial movement, affecting gear meshing accuracy, reducing transmission stability, and even causing abnormal bearing wear. In severe cases, this can lead to equipment failure.

[0003] In existing reducer structures, rigid structures such as retaining rings, snap rings, or limit sleeves are often used to limit the axial force generated by helical gears. Although these structures can suppress axial displacement to a certain extent, they lack elastic buffering and adjustment functions, making it difficult to adapt to clearance changes caused by load fluctuations, thermal expansion, manufacturing or assembly errors during operation. This can easily lead to problems such as structural loosening, increased noise, and inaccurate positioning. Utility Model Content

[0004] In view of this, the purpose of this utility model is to propose an axial positioning mechanism for helical gears in a vertical reducer, so as to solve the problem of axial force generated by helical gear meshing in existing reducers causing the input shaft to move.

[0005] To achieve the above objectives, this utility model provides an axial positioning mechanism for a helical gear in a vertical reducer, comprising: a housing, a worm gear rotatably mounted inside the housing, an output shaft fixedly mounted in the middle of the worm gear, a worm rotatably mounted on one side of the housing, the worm meshing with the worm gear, a second helical gear fixedly mounted on the worm, an input shaft rotatably mounted on one side of the housing, a first helical gear mounted on the input shaft, the first helical gear meshing with the second helical gear, and a positioning component provided on the input shaft, the positioning component being used to counteract the axial force generated when the first helical gear rotates.

[0006] Preferably, a plurality of fixed bearings are fixedly installed inside the housing, and the worm gear is rotatably installed between two of the fixed bearings.

[0007] Preferably, the output shaft is set at a 90-degree angle to the input shaft.

[0008] Preferably, the positioning component includes a tapered bushing that is interference-fitted with the input shaft, a plurality of disc springs are provided on the input shaft, a thrust bearing is installed on the side of the disc springs away from the first helical gear, an end cap is provided on the side of the thrust bearing away from the disc springs, and an installation groove is provided on one side of the interior of the housing, and the input shaft is rotatably installed in the installation groove.

[0009] Preferably, the first helical gear has an inner hole, the tapered bushing has a truncated cone structure, and the outer tapered surface of the tapered bushing is adapted to the inner hole.

[0010] Preferably, the concave surfaces of several disc springs contact the end face of the first helical gear, and they are arranged in an opposing combination.

[0011] Preferably, the end cap has several circular holes, and the end cap is threadedly connected to the mounting groove.

[0012] The beneficial effects of this utility model are:

[0013] 1. The helical gear axial positioning mechanism of this vertical reducer is provided with a conical bushing and a first helical gear. The conical bushing and the first helical gear form a self-locking structure through the conical surface cooperation. When subjected to axial load, the radial component force generated by the conical surface cooperation causes the contact surface pressure to automatically increase, effectively preventing axial displacement of the helical gear and ensuring transmission accuracy. At the same time, the interference fit between the conical bushing and the input shaft ensures the rigid connection of the overall structure.

[0014] 2. The axial positioning mechanism of the helical gear in this type of vertical reducer is equipped with disc springs. Several disc springs are arranged in opposite combinations. Their elastic characteristics can effectively buffer the impact load during operation. The direct contact between the disc springs and the end face of the first helical gear provides a continuous axial preload, which can automatically compensate for the clearance changes caused by wear or thermal deformation and extend the service life.

[0015] 3. The axial positioning mechanism of the helical gear in this type of vertical reducer is connected to the mounting groove of the housing by the end cover. The clamping force on the thrust bearing can be adjusted by rotating the end cover, thereby precisely controlling the compression of the disc spring assembly and realizing flexible adjustment of the axial clamping force of the helical gear to adapt to different working conditions.

[0016] 4. The helical gear axial positioning mechanism of this type of vertical reducer converts the rotational motion of the end cover into stable axial pressure by setting a thrust bearing between the disc spring and the end cover. At the same time, it isolates the relative motion between the rotating part and the stationary part, effectively reducing friction loss and improving the smoothness and reliability of operation. Attached Figure Description

[0017] To more clearly illustrate the technical solutions in this utility model or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only for this utility model. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0018] Figure 1 This is a first-view schematic diagram of the internal structure of this utility model;

[0019] Figure 2 This is a second-view schematic diagram of the internal structure of this utility model;

[0020] Figure 3 This is a cross-sectional structural diagram of the shell of this utility model;

[0021] Figure 4 This is a schematic diagram of the conical bushing, the first helical gear, and the disc spring of this utility model;

[0022] Figure 5 This is a cross-sectional structural diagram of the input shaft and the first helical gear of this utility model.

[0023] The diagram is marked as follows:

[0024] 1. Housing; 2. Output shaft; 3. Input shaft; 4. Mounting groove; 5. End cover; 6. Tapered bushing; 7. First helical gear; 8. Disc spring; 9. Thrust bearing; 10. Circular hole; 11. Worm gear; 12. Worm; 13. Second helical gear; 14. Fixed bearing; 15. Inner hole. Detailed Implementation

[0025] To make the objectives, technical solutions, and advantages of this utility model clearer, the present utility model will be further described in detail below with reference to specific embodiments.

[0026] It should be noted that, unless otherwise defined, the technical or scientific terms used in this utility model should have the ordinary meaning understood by one of ordinary skill in the art to which this utility model pertains. The terms "first," "second," and similar terms used in this utility model do not indicate any order, quantity, or importance, but are merely used to distinguish different components. Terms such as "comprising" or "including" mean that the element or object preceding the word encompasses the elements or objects listed following the word and their equivalents, without excluding other elements or objects. Terms such as "connected" or "linked" are not limited to physical or mechanical connections, but can include electrical connections, whether direct or indirect. Terms such as "upper," "lower," "left," and "right" are used only to indicate relative positional relationships; when the absolute position of the described object changes, the relative positional relationship may also change accordingly.

[0027] like Figures 1 to 5 As shown, the axial positioning mechanism of the helical gear in the vertical reducer includes: a housing 1, a worm gear 11 rotatably mounted inside the housing 1, an output shaft 2 fixedly mounted in the middle of the worm gear 11, a worm 12 rotatably mounted on one side of the housing 1, the worm 12 meshing with the worm gear 11, a second helical gear 13 fixedly mounted on the worm 12, an input shaft 3 rotatably mounted on one side of the housing 1, a first helical gear 7 mounted on the input shaft 3, the first helical gear 7 meshing with the second helical gear 13, a positioning component provided on the input shaft 3, the positioning component being used to counteract the axial force generated when the first helical gear 7 rotates; several fixed bearings 14 fixedly mounted inside the housing 1, the worm 12 rotatably mounted between two fixed bearings 14; the output shaft 2 and the input shaft 3 are set at a 90-degree angle.

[0028] This vertical reducer uses a motor or other drive source to rotate the input shaft 3. The first helical gear 7 mounted on the input shaft 3 rotates accordingly and meshes with the second helical gear 13 mounted on the worm 12, transmitting power from the input shaft 3 to the worm 12, thus achieving primary transmission. The worm 12 meshes with the worm wheel 11, and the rotation of the worm 12 drives the worm wheel 11 to rotate, thereby driving the output shaft 2, which is coaxially fixed with the worm wheel 11, to achieve output and complete the power reduction transmission. Since a certain axial force is generated during the meshing of the first helical gear 7 and the second helical gear 13, a positioning component is provided on the input shaft 3 to counteract the axial force generated when the first helical gear 7 rotates, preventing axial displacement of the input shaft 3 and ensuring the stability of the entire transmission process and the service life of the bearings. The worm 12 is supported by two fixed bearings 14 installed inside the housing 1, ensuring its rotational stability and the accuracy of meshing with the worm wheel 11. The input shaft 3 and the output shaft 2 of this vertical reducer are arranged at a 90-degree angle, which can achieve the purpose of compact structure, high-efficiency reduction and stable output.

[0029] like Figure 3 、 Figure 4 、 Figure 5As shown, the positioning assembly includes a tapered bushing 6 that is interference-fitted with the input shaft 3. Several disc springs 8 are mounted on the input shaft 3. A thrust bearing 9 is mounted on the side of the disc springs 8 away from the first helical gear 7. An end cover 5 is mounted on the side of the thrust bearing 9 away from the disc springs 8. A mounting groove 4 is provided inside one side of the housing 1, and the input shaft 3 is rotatably mounted in the mounting groove 4. An inner hole 15 is provided inside the first helical gear 7. The tapered bushing 6 has a truncated cone structure, and its outer conical surface is adapted to the inner hole 15. The concave surfaces of the disc springs 8 contact the end face of the first helical gear 7 and are arranged in a counter-facing combination. Several circular holes 10 are provided on the end cover 5, and the end cover 5 is threadedly connected to the mounting groove 4. When the vertical reducer operates, the input shaft 3 passes through... The tapered bushing 6 and the first helical gear 7 achieve axial positioning. The tapered bushing 6 and the input shaft 3 are fixedly connected by an interference fit. Its outer tapered surface and the inner hole 15 tapered surface of the first helical gear 7 form a self-locking structure. When the first helical gear 7 is subjected to axial load, the tapered surface engagement generates a radial component force, making the engagement tighter and tighter. The disc springs 8 are installed on the non-load-bearing side of the first helical gear 7 in an opposing combination arrangement. Their concave surfaces are in direct contact with the end face of the first helical gear 7, providing continuous axial preload to compensate for wear clearance. The thrust bearing 9 is located between the disc springs 8 and the end cover 5. When the end cover 5 is rotated for adjustment, the thrust bearing 9 converts the rotational movement of the end cover 5 into axial pressure and transmits it evenly to the disc spring 8 assembly, while preventing the disc springs 8 from rotating with the input shaft 3. Wear occurs; the end cap 5 is threaded and fits into the mounting groove 4 on the housing 1. Rotating the end cap 5 adjusts its clamping force on the thrust bearing 9, thereby controlling the compression of the disc spring 8 and the axial clamping degree of the first helical gear 7; the entire positioning assembly, through the synergistic effect of conical self-locking and elastic preload, ensures the axial positioning reliability of the first helical gear 7 while allowing micron-level floating to compensate for thermal deformation and assembly errors. The circular hole 10 on the end cap 5 facilitates tool turning for preload adjustment. It is worth mentioning that the arrangement of the disc spring 8 can be flexibly configured according to different application scenarios: in light-load operation or small gear transmission scenarios, 3 to 5 spring plates can be set, each spring plate acting in the same direction, and arranged in an overlapping manner. The structure can provide sufficient support and elasticity under light load conditions while ensuring the flexibility of the elastic system and avoiding mechanical wear caused by impact forces. In heavy-load operation or large gear drive scenarios, 6 to 8 spring plates are set in an opposing arrangement, that is, the action directions of adjacent spring plates are opposite. This opposing combination structure can effectively increase the rigidity of the system and improve the resistance to deformation, making it suitable for high-strength transmission environments. In mechanical structures with ultra-high precision requirements, 10 to 12 spring plates are set, and the spring plates are divided into multiple groups. Each group is arranged in the same direction and the different groups are arranged symmetrically. This structure can effectively balance the elastic forces in all directions while maintaining the overall elastic effect, reduce the phenomenon of off-center loading, and improve the stability and accuracy of equipment operation.

[0030] Those skilled in the art should understand that the discussion of any of the above embodiments is merely exemplary and is not intended to imply that the scope of the present invention (including the claims) is limited to these examples; within the framework of the present invention, the technical features of the above embodiments or different embodiments can also be combined, the steps can be implemented in any order, and there are many other variations of the different aspects of the present invention as described above, which are not provided in the details for the sake of brevity.

[0031] This utility model is intended to cover all such substitutions, modifications, and variations that fall within the broad scope of the appended claims. Therefore, any omissions, 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. An axial positioning mechanism for helical gears of a vertical speed reducer, characterized by, include: A housing (1) is rotatably mounted inside the housing (1). An output shaft (2) is fixedly mounted in the middle of the worm wheel (11). A worm (12) is rotatably mounted on one side of the housing (1). The worm (12) meshes with the worm wheel (11). A second helical gear (13) is fixedly mounted on the worm (12). An input shaft (3) is rotatably mounted on one side of the housing (1). A first helical gear (7) is mounted on the input shaft (3). The first helical gear (7) meshes with the second helical gear (13). A positioning component is provided on the input shaft (3). The positioning component is used to counteract the axial force generated when the first helical gear (7) rotates.

2. The helically toothed gear axial positioning mechanism of a vertical speed reducer according to claim 1, wherein The housing (1) is fixedly installed with several fixed bearings (14), and the worm gear (12) is rotatably installed between two of the fixed bearings (14).

3. The helically toothed gear axial positioning mechanism of a vertical speed reducer according to claim 2, wherein The output shaft (2) is set at a 90-degree angle to the input shaft (3).

4. The helically toothed gear axial positioning mechanism of a vertical speed reducer according to claim 1, wherein The positioning assembly includes a tapered bushing (6) that is interference-fitted with the input shaft (3). Several disc springs (8) are provided on the input shaft (3). A thrust bearing (9) is installed on the side of the disc springs (8) away from the first helical gear (7). An end cap (5) is provided on the side of the thrust bearing (9) away from the disc springs (8). An installation groove (4) is provided on one side of the interior of the housing (1). The input shaft (3) is rotatably installed in the installation groove (4).

5. The helical gear axial positioning mechanism of the vertical reducer according to claim 4, characterized in that, The first helical gear (7) has an inner hole (15) inside, and the conical bushing (6) has a truncated cone structure. The outer conical surface of the conical bushing (6) is adapted to the inner hole (15).

6. The helically toothed gear axial positioning mechanism of a vertical speed reducer according to claim 5, wherein The concave surfaces of several disc springs (8) are in contact with the end face of the first helical gear (7) and are arranged in an opposing combination.

7. The helically toothed gear axial positioning mechanism of a vertical speed reducer according to claim 6, wherein The end cap (5) has several round holes (10) and the end cap (5) is threadedly connected to the mounting groove (4).

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