Double worm heavy rotary speed reducer

Abstract

The utility model discloses a double worm heavy rotary speed reducer, including worm wheel, worm, casing, upper cover plate and drive arrangement. Worm wheel both sides symmetry set up with the meshing worm, and the both ends of worm are supported in casing through first bearing assembly, and the worm wheel is positioned through second bearing assembly on the upper and lower ends of worm gear. Casing is equipped with oil filler and sealing plug, and the contact place of worm wheel and casing is equipped with sealing strip. Drive arrangement is fixed in casing through connecting flange. The unique design of second bearing assembly can bear the axial and radial load of worm wheel, realize self-centering and the effect of improving stability, and the symmetrical layout of double worm greatly improves the carrying capacity and rigidity, and the end face bearing bears the axial force, and the needle bearing shares the radial load.

Description

Technical Field

[0001] This utility model relates to the field of mechanical transmission, specifically to a double worm gear heavy-duty rotary reducer. Background Technology

[0002] Traditional rotary reducers mostly employ a single worm gear driven worm wheel structure, which suffers from limited load-bearing capacity, susceptibility to uneven load distribution, and rapid bearing wear. Heavy equipment (such as mining machinery and port cranes) requires high-torque, high-stability reduction mechanisms, but existing structures struggle to meet the reliability requirements under long-term heavy-load conditions. Existing rotary reducers have the following drawbacks: 1. The meshing stress concentration of a single worm gear is prone to pitting or fracture on the tooth surface, making it difficult to meet heavy load requirements; 2. The equipment is prone to vibration during operation, resulting in low positioning accuracy. Traditional rotary reducers have poor vibration reduction effects. 3. Worm gear support bearings mainly bear radial forces, and their ability to bear axial loads is limited or insufficient, which can easily lead to axial movement and accelerated failure. Utility Model Content

[0003] The purpose of this invention is to overcome the defects in the existing technology and provide a double worm gear heavy-duty rotary reducer.

[0004] To achieve the above objectives, the technical solution of this utility model is to design a double worm gear heavy-duty rotary reducer, including a worm wheel, a worm, a housing, and a top cover plate. The worm wheel has symmetrically arranged worms meshing with it on both sides. The top cover plate is located above the housing and connected to the housing by bolts. First bearing assemblies are fitted at both ends of the worms, and the first bearing assemblies are mounted on the housing. A drive device is connected to one end of the worm, and the drive device is mounted on the housing via a connecting flange. An end cap is provided at one end of the first bearing assembly, and the end cap is connected to the housing by bolts. Second bearing assemblies are fitted at the upper and lower ends of the worm teeth of the worm wheel, and the second bearing assemblies are mounted on the housing. The first bearing assemblies can withstand the axial and radial loads of the worm, effectively preventing vibration under heavy loads. The second bearing assemblies, located on the worm wheel, effectively suppress worm wheel wobble and achieve self-centering. The combination of the first and second bearing assemblies improves the overall load-bearing capacity and stability of the equipment, and achieves vibration reduction and self-centering effects.

[0005] Specifically, the first bearing assembly includes a compression spring and a needle roller bearing sequentially mounted along the direction near the end of the worm. The compression spring can mitigate impacts and absorb vibrations, while the needle roller bearing bears the radial force of the worm and shares the radial load of the worm.

[0006] Furthermore, the first bearing assembly also includes an end face bearing, which is fitted between the compression spring and the needle roller bearing. The end face bearing bears the axial force of the worm and shares the axial load of the worm.

[0007] Specifically, the second bearing assembly includes an outer raceway ring, balls, and an inner raceway ring. The outer surface of the outer raceway ring is a right-angled surface, and the outer surface of the inner raceway ring is a tapered arc surface. Multiple sets of balls are evenly arranged within the outer and inner raceway rings. The inner raceway ring mates with the upper and lower axial surfaces of the worm gear teeth. The tapered arc surface of the inner raceway ring automatically adapts to the slight wobble or thermal expansion of the worm gear during operation and provides precise axial and radial guidance, thus achieving a self-centering effect. The right-angled surface of the outer raceway ring can bear the axial and radial loads of the worm gear, effectively improving the overall stability of the equipment.

[0008] Furthermore, sealing strips are provided at both ends of the worm gear where it contacts the housing and the upper cover plate. The sealing strips are preferably made of perfluoroether rubber, which prevents lubricant leakage and also prevents external dust and impurities from entering.

[0009] Furthermore, the housing is provided with an oil inlet, which penetrates the housing and communicates with the chamber where the worm gear is located. An oil plug is installed at the oil inlet. The oil inlet is used to inject lubricating oil or grease into the internal cavity of the housing containing the worm gear and worm wheel, thereby providing long-term lubrication protection for the reducer, helping to reduce wear, lower noise, improve accuracy and reliability, and extend the service life of components. The oil plug is used to seal the oil inlet.

[0010] Preferably, the driving device is a hydraulic motor. Hydraulic motors have high output torque and strong overload resistance.

[0011] The advantages and beneficial effects of this utility model are as follows: 1. The second bearing assembly, through its special structural design (the inner ring of the tapered raceway and the outer ring of the right-angle raceway), can bear the axial and radial loads of the worm gear, achieving self-centering and improving stability.

[0012] 2. The dual worm gear drive worm wheel can meet heavy load requirements; 3. The first bearing assembly and the second bearing assembly work together to effectively prevent vibration. Attached Figure Description

[0013] Figure 1 This is a schematic diagram of the reducer structure of this utility model; Figure 2 This is a schematic diagram of the internal structure of the speed reducer of this utility model; Figure 3 This is a sectional view of the speed reducer of this utility model; Figure 4This is a schematic diagram of the structure of the second bearing assembly of this utility model; Figure 5 This is a schematic diagram of the structure of the first bearing assembly of this utility model.

[0014] In the diagram: 1. Worm gear; 101. Worm tooth; 2. Worm; 3. Housing; 301. Oil inlet; 4. Top cover plate; 5. Bolt; 6. First bearing assembly; 601. Compression spring; 602. Needle roller bearing; 603. End face bearing; 7. Drive unit; 71. Connecting flange; 8. End cover; 9. Second bearing assembly; 901. Outer raceway ring; 902. Ball; 903. Inner raceway ring; 10. Sealing strip; 11. Oil inlet plug. Detailed Implementation

[0015] The specific embodiments of this utility model will be further described below with reference to the accompanying drawings and examples. The following examples are only used to more clearly illustrate the technical solution of this utility model and should not be construed as limiting the scope of protection of this utility model.

[0016] according to Figures 1-3 As shown, this utility model is a double worm gear heavy-duty rotary reducer, including a worm wheel 1, a worm 2, a housing 3, and an upper cover plate 4. The worm wheel 1 has worms 2 symmetrically arranged on both sides and meshing with it. The upper cover plate 4 is located above the housing 3 and is connected to the housing 3 by bolts 5. Both ends of the worm 2 are fitted with first bearing assemblies 6, which are mounted on the housing 3. The worm 2 is fitted on the first bearing assemblies 6. One end of the worm 2 is connected to a drive device 7, which is mounted on the housing 3 through a connecting flange 71. One end of the first bearing assembly 6 is provided with an end cap 8, which is connected to the housing 3 by bolts 5. The upper and lower ends of the worm teeth 101 of the worm wheel 1 are respectively fitted with second bearing assemblies 9, which are mounted on the housing 3.

[0017] The working principle is as follows: The drive device 7, connected to the worm gear 2, is activated, causing the worm gear 2 to rotate within the first bearing assembly 6. The worm gear 2 meshes with the worm wheel 1, thereby causing the worm wheel 1 to rotate slowly within the second bearing assembly 9. One end of the worm wheel 1 can be connected to the driven device via bolts 5 or other connecting parts, thus realizing power transmission. By combining the first bearing assembly 6 and the second bearing assembly 9, the overall load-bearing capacity and stability of the equipment can be improved, and vibration reduction and self-centering effects can be achieved.

[0018] according to Figure 5As shown, in any embodiment, the first bearing assembly 6 includes a compression spring 601 and a needle roller bearing 602 sequentially mounted along the direction near the end of the worm 2. The difference between this embodiment and other embodiments is that it includes a compression spring 601 and a needle roller bearing 602. The compression spring 601 can mitigate impacts and absorb vibrations, while the needle roller bearing 602 bears the radial force of the worm 2 and shares the radial load of the worm 2.

[0019] according to Figure 5 As shown, in any embodiment, the first bearing assembly 6 further includes an end face bearing 603, which is fitted between the compression spring 601 and the needle roller bearing 602. The difference between this embodiment and other embodiments is the inclusion of an end face bearing 603, which can withstand the axial force of the worm gear 2 and share the axial load of the worm gear 2.

[0020] according to Figure 4 As shown, in any embodiment, the second bearing assembly 9 includes an outer raceway 901, balls 902, and an inner raceway 903. The outer surface of the outer raceway 901 is a right-angled surface, and the outer surface of the inner raceway 903 is a tapered arc surface. Multiple sets of balls 902 are evenly arranged within the outer raceway 901 and the inner raceway 903. The inner raceway 903 mates with the upper and lower axial surfaces of the worm gear 101 of the worm wheel 1. The difference between this embodiment and other embodiments is that the tapered arc surface of the inner raceway 903 can automatically adapt to the slight wobble or thermal expansion of the worm wheel 1 during equipment operation and provide precise axial and radial guidance, thereby achieving a self-centering effect. The right-angled surface of the outer raceway 901 can bear the axial and radial loads of the worm wheel 1, effectively improving the overall stability of the equipment.

[0021] according to Figure 3 As shown, in any embodiment, sealing strips 10 are provided at both ends of the worm gear 1 where it contacts the housing 3 and the upper cover plate 4. The difference between this embodiment and other embodiments is that sealing strips 10 are provided at both ends of the worm gear 1 where it contacts the housing 3 and the upper cover plate 4. The sealing strips 10 are preferably made of perfluoroether rubber, which can prevent lubricant leakage and also prevent external dust and impurities from entering.

[0022] according to Figure 1 As shown, in any embodiment, the housing 3 has an oil inlet 301, which penetrates the housing 3 and communicates with the chamber where the worm gear 2 is located. An oil plug 11 is provided at the oil inlet 301. The difference between this embodiment and other embodiments is the presence of the oil inlet 301. The oil inlet 301 is used to inject lubricating oil or grease into the internal cavity of the housing 3 containing the worm gear 2 and worm wheel 1, thereby providing long-term lubrication protection for the reducer, helping to reduce wear, lower noise, improve accuracy and reliability, and extend the service life of components. The oil plug 11 is used to seal the oil inlet 301.

[0023] The drive device 7 is a hydraulic motor. The difference between this embodiment and other embodiments is that the drive device 7 is a hydraulic motor, which has a large output torque and strong overload resistance.

[0024] The above description is only a preferred embodiment of the present utility model. It should be noted that for those skilled in the art, several improvements and modifications can be made without departing from the technical principles of the present utility model, and these improvements and modifications should also be considered within the protection scope of the present utility model.

Claims

1. A heavy-duty slewing reducer with dual worm gears, comprising a worm wheel (1), a worm (2), a housing (3), and an upper cover plate (4), wherein worm gears (2) are symmetrically arranged on both sides of the worm wheel (1) and mesh with it, and the upper cover plate (4) is located above the housing (3) and connected to the housing (3) by bolts (5), characterized in that, Both ends of the worm (2) are fitted with first bearing assemblies (6), which are mounted on the housing (3). The worm (2) is fitted on the first bearing assembly (6). One end of the worm (2) is connected to a drive device (7), which is mounted on the housing (3) via a connecting flange (71). One end of the first bearing assembly (6) is provided with an end cap (8), which is connected to the housing (3) via bolts (5). The upper and lower ends of the worm teeth (101) of the worm wheel (1) are fitted with second bearing assemblies (9), which are mounted on the housing (3).

2. The heavy-duty double worm gear rotary reducer according to claim 1, characterized in that, The first bearing assembly (6) includes a compression spring (601) and a needle roller bearing (602) sequentially mounted along the direction close to the end of the worm (2).

3. The heavy-duty double worm gear rotary reducer according to claim 2, characterized in that, The first bearing assembly (6) further includes an end face bearing (603), which is fitted between the compression spring (601) and the needle roller bearing (602).

4. The heavy-duty double worm gear rotary reducer according to claim 1, characterized in that, The second bearing assembly (9) includes an outer raceway ring (901), balls (902), and an inner raceway ring (903). The outer surface of the outer raceway ring (901) is a right-angled surface, and the outer surface of the inner raceway ring (903) is a conical arc surface. The balls (902) are in multiple groups and are evenly arranged in the outer raceway ring (901) and the inner raceway ring (903). The inner raceway ring (903) is engaged with the upper and lower axial surfaces of the worm gear (101) of the worm wheel (1).

5. A heavy-duty double worm gear rotary reducer according to claim 1, characterized in that, Sealing strips (10) are provided at both ends of the worm gear (1) where it contacts the housing (3) and the upper cover plate (4).

6. The heavy-duty double worm gear rotary reducer according to claim 1, characterized in that, The housing (3) is provided with an oil inlet (301), which penetrates the housing (3) and communicates with the chamber where the worm (2) is located. An oil plug (11) is provided at the oil inlet (301).

7. A heavy-duty double worm gear rotary reducer according to claim 1, characterized in that, The drive device (7) is a hydraulic motor.

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