Efficient heat dissipation worm gear and worm helical gear speed reduction motor for light-load machinery

Abstract

The invention relates to the technical field of gear motors, in particular to an efficient heat dissipation worm gear and worm helical gear gear motor for light-load machinery, which comprises a box body, and the box body is provided with stepped holes for mounting a bearing and an end cover and outer surface reinforcing ribs for external heat dissipation; the motor unit is fixedly connected with the box body; and the composite transmission mechanism at least comprises a parallel shaft gear stage and a staggered shaft transmission pair. Compared with the prior art, the composite transmission of one-stage bevel gear and one-stage worm gear and worm is arranged, and the conical roller bearing, the output shaft deep groove ball bearing and the distance ring / elastic check ring which are arranged at the two ends of the worm shaft in a back-to-back mode are used for axial limiting; and a first metal adjusting pad and a second metal adjusting pad are matched to perform decoupling quantitative adjustment on the meshing backlash and the bearing pre-tightening amount, so that the effects of obtaining a large transmission ratio and smooth output in a compact volume, and giving consideration to both high axial rigidity and low noise are achieved.

Description

Technical Field

[0001] This invention relates to the field of geared motor technology, and in particular to a high-efficiency heat-dissipating worm gear helical gear geared motor for light-load machinery. Background Technology

[0002] Worm gear and helical gear compound geared motors are widely used in food packaging, logistics sorting, light conveying, and general light-load equipment due to their compact size, wide transmission ratio range, and stable output. Traditional products mostly adopt a basic structure of "integrated housing + helical gear single-stage reduction + worm gear single-stage reduction". The housing is mainly lubricated by oil immersion / splash, and the input end usually uses an end cover + washer or simple labyrinth seal. The output end is usually equipped with a skeleton oil seal. The worm is supported by bearings at both ends. During assembly, the meshing backlash and bearing preload are initially set by adjusting shims or end face clearance.

[0003] In the prior art, Chinese patent document CN109469710B, concerning a worm gear reducer motor, proposes that the left and right fixed flanges can be fixed together using multiple sets of fixing brackets, multiple sets of fixing threaded rods, and multiple sets of fixing nuts, thereby stably fixing the motor to the right side wall of the housing. Simultaneously, the motor's power is transmitted to the connecting gear via a drive shaft. Because the connecting gear meshes with the drive gear, the worm can be driven to rotate even when the motor and worm are not on the same axis, thus improving the motor's installation stability. However, consistent with traditional methods, existing engineering approaches typically focus on achieving versatility and consistency by expanding the reduction ratio coverage, improving tooth surface hardness and machining accuracy, and optimizing the housing shape and ribs. While the heat dissipation capacity is fixed, in application scenarios such as long-term continuous operation, frequent start-stop, or high ambient temperature, issues such as meshing heat, oil temperature peaks, seal leakage, and assembly consistency still affect efficiency and lifespan. At the same time, due to the relatively coarse organization of the oil and air circuits and insufficient thermo-mechanical coupling design, phenomena such as meshing center drift with temperature rise, noise increase, and high maintenance costs occur frequently. Therefore, the industry urgently needs to make systematic improvements in aspects such as "quantitative controllable backlash / preload, coordinated heat dissipation of oil and air circuits, seal maintainability, and all-position adaptability" to achieve higher transmission efficiency, thermal stability, and full-life reliability within a compact volume. Therefore, this application discloses a high-efficiency heat dissipation worm gear helical gear reducer motor for light-load machinery. Summary of the Invention

[0004] In view of this, the purpose of this invention is to propose a high-efficiency heat-dissipating worm gear helical gear reducer motor for light-load machinery, so as to solve the bottleneck problems of traditional composite gear motors under long-term high temperature / frequent start-up conditions, such as meshing heat and oil temperature peaks, leakage and assembly discrepancies, insufficient thermo-mechanical coupling leading to center drift and noise increase.

[0005] To achieve the above objectives, the present invention provides a high-efficiency heat-dissipating worm gear helical gear reducer motor for light-load machinery, including a housing, the housing having stepped holes for mounting bearings and end covers and outer surface reinforcing ribs for external heat dissipation; A motor unit, which is fixedly connected to the housing; The composite transmission mechanism includes a parallel shaft helical gear transmission stage installed in the input cavity of the housing, and a worm gear transmission pair installed in the output cavity of the housing, which is formed by the alternating meshing of the worm body and the worm wheel body. The parallel shaft helical gear transmission stage is used to realize the primary speed reduction and torque transmission of the motor unit, and the worm gear transmission pair further reduces the speed and outputs it to the output shaft. An axial positioning assembly is provided to withstand radial / axial loads generated by the transmission mechanism and to achieve axial positioning. The axial positioning assembly includes: tapered roller bearings arranged facing each other at both ends of the worm gear body; a deep groove ball bearing on the output shaft; and a spacer ring, a shaft elastic retaining ring, and a bore elastic retaining ring for axial limiting / positioning. It also includes a first adjusting shim located between the end face of the worm gear body and the axial support surface of the housing, near the sight glass cover, for adjusting the worm gear-worm meshing backlash; and a second adjusting shim located between the cover and the outer ring of the tapered roller bearing, for adjusting the worm gear bearing preload. The lubrication and heat dissipation assembly and the sealing assembly are provided. The lubrication and heat dissipation assembly is located in the lower oil sump and end cover area of ​​the housing and is used to splash lubricate and remove heat from the transmission pair and bearings. The sealing assembly is located at the input end cover and the output end cover and is used to seal and isolate the motor input side and the extended end of the output shaft.

[0006] Preferably, the parallel shaft gear stage is a helical gear transmission, specifically including an input driving gear mounted on the motor shaft and an input driven gear meshing with the input driving gear; the staggered shaft transmission pair includes a worm gear and a worm wheel meshing with a worm body and a worm wheel body, the input driven gear being coaxially driven and connected to the worm body, the worm body being arranged along the transverse direction of the housing and supported at both ends of the housing by tapered roller bearings; the worm wheel body being arranged along the longitudinal direction of the housing and fixedly connected to the output shaft, its hub end face abutting against the axial support surface of the housing through a first adjusting shim, thereby realizing the staggered arrangement and meshing transmission of the worm and worm wheel within the output cavity of the housing.

[0007] Preferably, the worm gear body is rotatably mounted in a symmetrical bearing housing of the housing via tapered roller bearings at both ends, and the two tapered roller bearings are arranged facing each other to withstand the bidirectional axial force generated by the meshing of the worm gear; The output shaft is rotatably mounted in the output end bearing seat of the housing via a deep groove ball bearing, and is axially limited by a spacer ring and an elastic retaining ring.

[0008] Preferably, the input driven gear engages with a keyway on the worm gear journal via a keyway in the gear's inner hole, and is embedded between the two via a first ordinary flat key; the worm gear body engages with a keyway on the outer circle of the output shaft via a keyway in its inner hole, and is embedded between the two via a second ordinary flat key; the worm gear-worm meshing backlash is adjusted by changing the thickness of a first adjusting shim located between the end face of the worm gear body and the housing support surface; the worm bearing preload is adjusted by changing the thickness of a second adjusting shim located between the cover and the outer ring of the tapered roller bearing, wherein the first and second adjusting shims are metal adjusting shims.

[0009] Preferably, the lubrication and heat dissipation assembly includes: An oil baffle ring is installed adjacent to the worm body. The oil baffle ring forms a guide edge along the circumference. During operation, it throws the oil towards the worm-worm wheel meshing area and the bearing areas on both sides. The oil return channel and / or spiral guide ribs on the inner wall of the tank are provided, and the channel guides the oil back to the oil pool at the bottom of the tank through the meshing area and the bearing area. The vent plug located at the top of the housing is used to balance the pressure inside and outside the housing and to suppress the escape of oil mist caused by temperature rise. The sight glass cover, located on the side wall of the tank at the normal oil level, is used to observe the oil level and oil quality in real time. The oil plug, located at the lowest point of the bottom of the housing, is used for draining oil and maintenance. The outer surface of the enclosure features integrally formed heat dissipation reinforcing ribs and / or sheet-like heat dissipation surfaces; Among them, the oil baffle ring, oil return channel, inner wall spiral guide rib, vent plug, sight glass cover and oil plug together in space along the direction of gravity to form a partitioned structure of upper air chamber and lower oil chamber. During operation, the oil heats the tooth surface and bearing friction heat to the housing, and after being cooled by surface flow on the outer surface, it flows back to the oil sump.

[0010] Preferably, the sealing assembly includes: The input side has a non-contact seal, which is formed by the fit of a cover and a gasket. The gasket is embedded between the cover and the input shaft and defines a multi-level annular gap labyrinth channel at the input end of the housing. A set gap is maintained between the rotating surface of the input shaft end and the cover. The contact seal on the output side is formed by a double-lip oil seal press-fitted into the stepped hole at the output end of the housing or into the end hole of the cover. The double-lip oil seal faces the oil cavity side and seals against the polished running-in surface of the output shaft. The elastic retaining rings for the holes are located at the end steps of the input and output ends of the housing, respectively, to axially limit the oil seal or end cover.

[0011] Preferably, the vent plug is located on the upper surface of the housing and is higher than the tip circle of the worm gear body in the vertical direction. The vent plug is equipped with an anti-oil return structure and a breathable one-way valve, and a replaceable oil mist collection core is provided in the ventilation path.

[0012] Preferably, the outer wall of the housing near the worm gear body is provided with a thickened heat-conducting rib area, the inner side of the thickened heat-conducting rib area corresponds to the meshing area of ​​the worm gear body, and the outer side forms a sheet-like heat dissipation surface; the oil baffle ring is located at a splash radius position larger than the pitch circle radius of the worm gear body, so that the splashed oil first covers the tooth surface of the worm body and then falls back to the tooth surface of the worm gear body, so as to preferentially cool the high-heat area; the inner wall of the housing forms a spiral guide rib along the axial direction of the worm body, which is consistent with the rotation direction of the worm, and is used to push the oil to the bearing areas at both ends.

[0013] Preferably, the worm gear body adopts a hardened tooth surface structure with carburizing and quenching and precision grinding, the worm wheel body is made of zinc-based alloy or aluminum bronze, and the input driving gear and the input driven gear are helical gears with carburizing and quenching and grinding.

[0014] Preferably, a replaceable thin-walled bushing is provided at the output side seal as the running-in surface of the double-lip oil seal. The outer circle of the bushing forms multiple staggered running-in areas in a circumferentially segmented manner. During maintenance, the sealing surface can be renewed by rotating or replacing the bushing. Furthermore, under different installation postures, the above-mentioned lubrication and sealing components still maintain the partitioned structure of the upper air chamber and the lower oil chamber to ensure a stable oil level and low leakage.

[0015] The beneficial effects of this invention are: 1. This type of high-efficiency heat-dissipating worm gear helical gear reducer motor for light-load machinery utilizes a composite transmission consisting of a "helical gear stage + worm gear stage." Axial limiting is achieved through tapered roller bearings arranged back-to-back at both ends of the worm shaft, deep groove ball bearings on the output shaft, and spacer rings / elastic retaining rings. Furthermore, the first / second metal adjusting shims decouple and quantify the meshing backlash and bearing preload, resulting in a large transmission ratio and smooth output within a compact volume, while maintaining high axial stiffness and low noise. Assembly consistency is quantifiable and controllable by "thickness," ensuring stable contact spots and backlash, reducing vibration and meshing heat caused by assembly deviations, and providing a stable benchmark for subsequent heat dissipation and sealing performance, thus comprehensively improving efficiency and lifespan.

[0016] 2. This type of high-efficiency heat-dissipating worm gear helical gear reducer motor for light-load machinery achieves the following effects: by setting up an oil baffle ring + inner wall return channel / spiral guide ribs and a thickened heat-conducting rib area / plate-shaped heat dissipation surface opposite to the meshing of the worm gear, and arranging the static oil level, vent plug, sight glass cover, and drain plug in a "upper air chamber - lower oil chamber" partition, a passive circulation oil circuit and a high-efficiency heat-conducting channel are formed during operation, which prioritizes cooling the high-heat meshing area and the bearings at both ends, reduces oil temperature peak and stirring loss, and maintains oil film continuity and contact spot stability. Thermal deformation and meshing drift are suppressed, and efficiency and reliability are significantly improved under long-term continuous operation. It also forms a stable thermo-mechanical coupling system with the precise setting of the upstream side clearance / preload.

[0017] 3. This type of high-efficiency heat-dissipating worm gear helical gear reducer motor for light-load machinery achieves low leakage, low pollution, and low wear even under multi-position installation and pressure pulsation. It features a non-contact labyrinth seal at the input end, a double-lip oil seal at the output end, and an end-limiting elastic retaining ring for the bore. A replaceable thin-walled bushing is added at the output end as a running-in surface. At the same time, a breathable one-way valve and an oil mist collection core are arranged in the ventilation path. The oil seal running-in surface can be reused in a staggered manner or quickly replaced, significantly reducing downtime and maintenance costs. Combined with the aforementioned stable transmission stiffness and oil circuit heat dissipation, a closed-loop reliability system is formed from the tooth surface to the seal, enabling the whole machine to maintain the comprehensive advantages of high efficiency, low failure rate, and easy maintenance throughout its entire life cycle. Attached Figure Description

[0018] To more clearly illustrate the technical solutions in this invention 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 invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0019] Figure 1 This is a schematic diagram of the internal first-view cross-sectional structure of the present invention; Figure 2 This is a schematic diagram of the internal second-view cross-sectional structure of the present invention; Figure 3 This is a schematic diagram of the working process of the axial positioning system of the present invention; Figure 4 This is a schematic diagram of the lubrication and heat dissipation circulation process of the present invention; Figure 5 This is a schematic diagram of the collaborative process of the sealing component of the present invention.

[0020] The diagram is marked as follows: 1. Motor unit; 2. Input driven gear; 3. Input driving gear; 6. Breath plug; 7. Sight hole cover; 8. First adjusting shim; 9. Worm gear body; 10. Housing; 11. Cover; 12. Hole retaining ring; 13. Washer; 14. Second adjusting shim; 15. Tapered roller bearing; 16. Oil retaining ring; 17. Worm body; 18. First ordinary flat key; 19. Shaft retaining ring; 20. Oil plug; 21. Spacer ring; 22. Deep groove ball bearing; 24. Double lip oil seal; 25. Second ordinary flat key; 26. Output shaft. Detailed Implementation

[0021] To make the objectives, technical solutions, and advantages of this invention clearer, the invention will be further described in detail below with reference to specific embodiments.

[0022] It should be noted that, unless otherwise defined, the technical or scientific terms used in this invention should have the ordinary meaning understood by one of ordinary skill in the art to which this invention pertains. The terms "first," "second," and similar terms used in this invention 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.

[0023] like Figures 1 to 5As shown, a high-efficiency heat-dissipating worm gear helical gear reducer motor for light-load machinery includes: a housing 10, which has stepped holes for mounting bearings and end covers, and reinforcing ribs on the outer surface for external heat dissipation; a motor unit 1, which is fixedly connected to the housing 10; and a composite transmission mechanism, which includes a parallel shaft helical gear transmission stage installed in the input cavity of the housing 10, and a worm gear transmission pair installed in the output cavity of the housing 10, which is formed by the staggered meshing of the worm body 17 and the worm wheel body 9. The parallel shaft helical gear transmission stage is used to realize the primary speed reduction and torque transmission of the motor unit 1, while the worm gear transmission pair further reduces the rotational speed and outputs it to the output shaft 26; axial The positioning assembly, specifically the axial positioning assembly, is used to withstand the radial / axial load generated by the transmission mechanism and achieve axial positioning. The axial positioning assembly includes: tapered roller bearings 15 arranged facing each other at both ends of the worm gear body 17; a deep groove ball bearing 22 mounted on the output shaft 26; and a spacer ring 21, a shaft elastic retaining ring 19, and a bore elastic retaining ring 12 for axial limiting / positioning. It also includes a first adjusting shim 8 located between the end face of the worm gear body 9 and the axial support surface of the housing 10, near the viewing cover 7, for adjusting the worm gear-worm meshing backlash; and a second adjusting shim 14 located between the cover 11 and the outer ring of the tapered roller bearing 15, for adjusting the worm gear meshing backlash. The preload of the rod bearing; the lubrication and heat dissipation assembly and the sealing assembly, the lubrication and heat dissipation assembly is set in the lower oil sump and end cover area of ​​the housing 10, used for splash lubrication and heat removal of the transmission pair and bearing; the sealing assembly is set at the input end cover and output end cover, used for sealing and isolating the motor input side and the extended end of the output shaft 26, wherein the parallel shaft gear stage is a helical gear transmission, specifically including the input driving gear 3 set on the motor shaft, and the input driven gear 2 meshing with the input driving gear 3; the interleaved shaft transmission pair includes a worm gear and worm body 17 meshing with the worm wheel body 9, the input driven gear 2 is coaxially driven and connected to the worm body 17, and the worm body 17 is set along the transverse direction of the housing 10. The worm gear body 9 is positioned and supported at both ends of the housing 10 by tapered roller bearings. The worm gear body 9 is arranged along the longitudinal direction of the housing 10 and is fixedly connected to the output shaft 26. Its hub end face abuts against the axial support surface of the housing 10 through the first adjusting shim 8, thereby realizing the staggered arrangement and meshing transmission of the worm and worm wheel in the output cavity of the housing 10. The worm gear body 17 is rotatably mounted in the symmetrical bearing seat of the housing 10 through tapered roller bearings 15 at both ends. The two tapered roller bearings 15 are arranged facing each other to bear the bidirectional axial force generated by the meshing of the worm. The output shaft 26 is rotatably mounted in the output end bearing seat of the housing 10 through deep groove ball bearings 22 and is axially limited by a spacer ring 21 and a shaft elastic retaining ring 19. The composite geared motor is a universal type for vertical or horizontal mounting. The tapered roller bearings 15 at both ends of the worm shaft are arranged back-to-back (DB) to obtain higher axial stiffness. The deep groove ball bearing 22 at the output shaft 26 end is an interference fit to bear radial force. The housing 10 is connected to the motor using a B5 flange or a direct-connect end cover. The reinforcing ribs on the outer surface of the housing 10 are arranged in the main heat dissipation direction to improve the natural convection heat dissipation efficiency while taking into account rigidity / weight. The motor unit 1 is directly connected to the housing 10 via a flange. The input drive gear 3 drives the input driven gear 2 to complete the first-stage speed reduction, and then coaxially drives the worm gear to mesh with the worm wheel to achieve the second-stage speed reduction. The worm shaft is supported by tapered roller bearings 15 at both ends and preloaded by the second adjusting shim 14. The output shaft 26 is supported by deep groove ball bearings 22 and axially limited by the spacer ring 21 / retaining ring. During assembly, the worm wheel-worm clearance is first set with the first adjusting shim 8, and then the bearing preload is set with the second adjusting shim 14. After checking the contact spots and no-load noise, the cover 11 is sealed. During operation, the lubrication and heat dissipation components establish an oil circuit of "splash-return-resplash" inside the housing. The sealing components isolate the oil circuit from the outside to ensure long-term stable operation. A compound reduction of "helical gear first stage + worm gear first stage" is adopted. The front-stage helical gear transmission is highly efficient and low-noise, while the rear-stage worm gear has a large transmission ratio and self-locking characteristics. The two are coupled within the same housing 10, achieving a large reduction ratio and smooth output within a compact volume. Reinforcing ribs on the outer surface of the housing 10 enhance heat dissipation and overall rigidity, reducing the impact of thermal deformation on meshing. Tapered roller bearings 15 at both ends of the worm are arranged facing each other, providing high axial rigidity and the ability to withstand thrust in both directions. The output shaft 26 uses a deep groove ball bearing 22 to bear the radial load, with a spacer ring 21 and an elastic retaining ring for limiting the position. The structure is simple and easy to assemble and disassemble. Two metal adjusting shims decouple "side clearance" and "preload" into quantitatively adjustable parameters, facilitating batch assembly consistency control. The entire machine achieves a balance between rigidity, heat dissipation, and adjustable assembly, improving lifespan and reliability.

[0024] like Figures 1 to 3 As shown, the input driven gear 2 engages with the keyway on the journal of the worm gear body 17 via a keyway in the gear's inner hole, and is embedded between the two via a first ordinary flat key 18; the worm gear body 9 engages with the keyway on the outer circle of the output shaft 26 via a keyway in its inner hole, and is embedded between the two via a second ordinary flat key 25; the worm gear-worm meshing clearance is adjusted by changing the thickness of the first adjusting shim 8 located between the end face of the worm gear body 9 and the support surface of the housing 10; the worm bearing preload is adjusted by changing the thickness of the second adjusting shim 14 located between the cover 11 and the outer ring of the tapered roller bearing 15, and the first adjusting shim 8 and the second adjusting shim 14 are metal adjusting shims; In one embodiment, the first ordinary flat key 18 and the second ordinary flat key 25 are selected according to GB / T 1096. The key and keyway fit tolerance adopts N9 / P9. The worm gear-worm meshing backlash is finely adjusted by the thickness of the first adjusting shims (8 pieces), with a recommended target backlash of 0.06–0.18 mm (measured at the pitch circle). The adjusting shims are made of stainless steel or phosphor bronze, with thicknesses of 0.02, 0.05, 0.10, and 0.20 mm that can be combined and stacked, with the total thickness difference controlled within ±0.01 mm. The bearing preload is set by the second adjusting shim (14), with an axial preload displacement of 0.02–0.08 mm (checked by the bearing starting torque or temperature rise method). The assembly sequence is: initial assembly—blueing inspection—backlash measurement—shim replacement / stacking—reassembly—retest. The torque locking sequence is performed diagonally in steps, ultimately covering 60%–80% of the tooth surface length and 40%–60% of the tooth height with contact spots. For compliance standards, the standardized connection of the first ordinary flat key 18 and the second ordinary flat key 25 ensures reliable torque transmission and convenient processing / replacement; the first adjusting shim 8 is used to independently correct the worm gear-worm backlash, adjusting the meshing from being too tight / heating or too loose / knocking to the optimal point of overall noise and efficiency; the second adjusting shim 14 is used to independently set the preload of the tapered roller bearing 15, eliminating axial clearance and avoiding excessive preload that leads to temperature rise and wear; the two shims change the assembly sensitivity from "worker's feeling" to "thickness quantification", significantly improving consistency and maintainability.

[0025] like Figure 1 , Figure 2 , Figure 4 As shown, the lubrication and heat dissipation assembly includes: The oil baffle ring 16 is located adjacent to the worm body 17. The oil baffle ring 16 forms a guide edge along the circumference. During operation, it throws the oil towards the worm-worm wheel meshing area and the bearing areas on both sides. The oil return channel and / or spiral guide ribs on the inner wall of the housing 10 guide the oil back to the bottom oil sump of the housing from the meshing area and the bearing area. The vent plug 6 located on the upper part of the housing 10 is used to balance the pressure inside and outside the housing 10 and suppress the escape of oil mist caused by temperature rise. The sight glass cover 7, located on the side wall of the housing 10 at the normal oil level, is used to observe the oil level and oil quality in real time. The oil plug 20, located at the lowest point of the bottom of the housing 10, is used for draining oil and maintenance. The outer surface of the enclosure 10 features integrally formed heat dissipation reinforcing ribs and / or sheet-like heat dissipation surfaces; Among them, the oil baffle ring 16, oil return channel, inner wall spiral guide rib, vent plug 6, sight glass cover 7 and oil plug 20 together define the partition structure of the upper air chamber and the lower oil chamber in space along the direction of gravity. During operation, the oil heats the tooth surface and bearing friction heat to the housing 10, and after heat dissipation through the outer surface convection, it flows back to the oil sump. The static oil level is set to 1 / 3 to 1 / 2 of the pitch circle diameter of the worm gear. The cross-sectional area of ​​the oil return channel on the inner wall of the housing 10 is 30 to 80 mm², and a longitudinal slope of 1° to 3° is set to guide the return flow to the oil sump. The spiral guide ribs on the inner wall are consistent with the rotation direction of the worm gear, and the lead is 0.8 to 1.2 times the lead of the worm gear, so as to direct the splashed oil to the bearing areas at both ends. The guide edge height of the oil baffle ring 16 is 1.0 to 1.5 mm, and the outer diameter falls at a position larger than the pitch circle radius of the worm gear, giving priority to covering the high-heat meshing area. The vent plug 6 on the upper surface of the housing 10 is used for thermal expansion balance and to reduce oil mist escape. The side wall sight glass cover 7 is located at the static oil level ±5 mm for inspection. The bottom drain plug 20 is set at the lowest point for easy maintenance. If necessary, an external fan or a mini plate-fin heat exchanger can be added to enhance convection. The oil baffle ring 16 directs splashed oil towards the meshing area and bearing area, improving oil film coverage efficiency and prioritizing cooling of high heat sources. The inner wall return channel / spiral guide ribs construct a passive circulation oil circuit, reducing stirring losses and oil temperature peaks. The vent plug 6 balances the internal and external pressure difference and suppresses oil mist escape caused by the "breathing effect". The sight glass cover 7 facilitates quick inspection of oil level / oil quality without stopping the machine. The oil plug 20 is placed at the lowest point for thorough oil draining. The heat dissipation ribs of the housing 10 increase the convection area and, together with the oil circuit circulation, form an efficient heat-carrying chain of oil-wall-air. A thickened heat-conducting rib area is provided on the outer wall of the housing 10 near the worm gear body 9. The inner side of the thickened heat-conducting rib area corresponds to the meshing area of ​​the worm gear body 9, and the outer side forms a sheet-like heat dissipation surface. The oil baffle ring 16 is located at a splash radius position that is larger than the pitch circle radius of the worm gear body 9, so that the splashed oil first covers the tooth surface of the worm body 17 and then falls back to the tooth surface of the worm gear body 9, so as to preferentially cool the high-heat area. The inner wall of the housing 10 preferably forms a spiral guide rib that is consistent with the rotation direction of the worm along the axial direction of the worm body 17, which is used to push the oil to the bearing areas at both ends. The outer wall of the worm gear meshing area is thickened with heat-conducting ribs, which are 1.5–2.0 mm thicker than the surrounding area. The outer side forms a sheet-like heat dissipation surface, with a single sheet width of 12–18 mm and a spacing of 10–15 mm. The inner wall has spiral guide ribs with a height of 0.8–1.5 mm, a top width of 1.0–2.0 mm, and a fillet radius of R0.5 to reduce oil film shear resistance. The ends of the guide ribs form a collecting groove (2–3 mm deep) at the bearing cavity, allowing the return oil to preferentially wet the rollers and cage. The combination of the oil baffle ring 16 and the guide ribs ensures that splashed oil first covers the worm gear tooth tip and engagement point, then falls back to the worm gear tooth surface and is delivered to the bearing via the ribs, realizing a closed-loop heat exchange path of "meshing—bearing—oil sump".

[0026] like Figure 1 , Figure 2 , Figure 5 As shown, the sealing assembly includes: The sealing assembly includes: The input side has a non-contact seal, which is formed by the fit of the cover 11 and the gasket 13. The gasket 13 is embedded between the cover 11 and the input shaft, and a multi-level annular gap labyrinth channel is defined at the input end of the housing 10. A set gap is maintained between the rotating surface of the input shaft end and the cover 11. The contact seal on the output side is formed by a double-lip oil seal 24 press-fitted into the stepped hole at the output end of the housing 10 or into the end hole of the cover 11. The double-lip oil seal 24 faces the oil cavity side and seals against the polished running surface of the output shaft 26. Among them, the elastic retaining rings 12 for the holes are located at the end steps of the input end and the output end of the housing 10, respectively, to axially limit the oil seal or end cover; The input-side labyrinth seal consists of a cap 11 and a washer 13 forming 3-5 levels of annular gaps, with a single-level gap of 0.2-0.5 mm and a total axial length ≥6 mm. The labyrinth cavity has an oil return groove leading into the housing to reduce external leakage. The output side uses a double-lip oil seal 24 (material FKM70-80 Shore A, with a stainless steel spring), with the lip facing the oil side. The mating journal (or bushing) has a surface roughness Ra≤0.2μm, hardness ≥55HRC, and circular runout ≤0.03mm. An elastic retaining ring 12 is located at the end step of the bore for axial limiting, preventing... To prevent end caps or oil seals from shifting under thermal shock / pulsating pressure, for positive pressure conditions, the labyrinth final stage can be equipped with an oil drain hole connected to the vent plug 6 to avoid pressure buildup inside the cavity. The input end uses a non-contact labyrinth, which has almost zero friction, high temperature resistance, and long service life. The output end uses a contact double-lip oil seal 24, with the inner lip preventing leakage and the outer lip preventing dust, resulting in good overall sealing performance. The orifice uses an elastic retaining ring 12 as an end limit to prevent end caps or oil seals from shifting and causing sealing failure. The zoned sealing stabilizes the "upper air cavity - lower oil cavity", reducing leakage rate and contamination risk. A replaceable thin-walled bushing is provided at the output side seal as the running surface of the double-lip oil seal 24. The outer circle of the bushing forms multiple running areas that can be misaligned and used in a circumferentially segmented manner. During maintenance, the sealing surface can be renewed by rotating or replacing the bushing. Furthermore, under different installation postures, the above-mentioned lubrication and sealing components still maintain the partitioned structure of the upper air chamber and the lower oil chamber to ensure a stable oil level and low leakage. A replaceable thin-walled bushing is provided at the output end as the oil seal running-in surface, allowing for staggered or quick replacement, significantly extending the total seal life and reducing downtime costs. Multi-stage running-in zones distribute wear, reducing irreversible damage to the main journal. Furthermore, even with changes in equipment installation orientation, the 10-zone enclosure (upper air chamber – lower oil chamber) and built-in oil return path maintain a stable oil level and low leakage, offering good environmental adaptability. When using the replaceable thin-walled bushing on the output side as the oil seal running-in surface, the bushing material is 40Cr nitrided (or stainless steel with laser hardening), with a surface hardness of HV 700–900 and a depth of 0.2–0.4 mm; wall thickness of 0.5–1.2 mm, and an H7 / u6 interference fit with the shaft of 0.01–0.03 mm. Anaerobic adhesive (such as 648) can be used to prevent loosening during assembly. The outer circumference of the bushing is divided into 4–6 "usable running-in zones," which can be adjusted at 60°–90° during maintenance. The misaligned rotation can be used for continued operation; when the wear groove width is >1.5 mm or the depth is >0.05 mm, it is recommended to replace it. The recommended oil seal size is 25×47×7 (example). Install it with the help of a special mandrel and apply an appropriate amount of grease to avoid dry friction and groove formation. This structure significantly extends the seal life and reduces downtime costs. Furthermore, under different installation postures, such as horizontal installation (output shaft horizontal), vertical installation (output shaft downward), vertical installation (output shaft upward), and lateral installation, the structure of the housing 10 can ensure that the lubrication and sealing components maintain the partitioned relationship of "upper air chamber - lower oil chamber", the oil can always maintain a stable oil level, and the sealing effect of the oil seal and the bushing is not weakened due to changes in posture, thereby ensuring the sealing life and lubrication and heat dissipation effect.

[0027] like Figure 1 , Figure 2 As shown, the vent plug 6 is located on the upper surface of the housing 10 and is higher than the tooth tip circle of the worm gear body 9 in the vertical direction. The vent plug 6 is equipped with an anti-oil return structure and a breathable one-way valve, and a replaceable oil mist collection core is provided in the ventilation path. The vent plug 6 is located on the upper surface of the housing 10, with a geometric height higher than the tip circle of the worm gear teeth. It is equipped with a breathable one-way valve with an opening pressure of 3–8 kPa, ensuring smooth exhaust during temperature rise and slow intake during cooling, reducing the intake of external moisture / dust. The ventilation path is connected in series with a replaceable oil mist trap (glass fiber or sintered metal, filtration accuracy 0.3–1 μm), and an anti-backflow baffle prevents splashed oil from directly impacting the filter element. It is recommended to replace it every 2000–4000 hours or when the pressure drop is ≥5 kPa. The vent plug 6 housing is reliably grounded to the housing 10 to prevent static electricity accumulation from causing oil mist fire. The vent plug 6's location above the tip circle of the teeth effectively prevents direct impact from splashed oil. The built-in breathable one-way valve balances the pressure difference inside and outside the housing, preventing the introduction of moisture and dust through "inhalation," reducing emulsification and wear. The oil mist trap intercepts fine oil mist, reducing environmental pollution and oil consumption. The anti-backflow structure prevents oil from overflowing through the vent holes, improving overall cleanliness and safety. The worm body 17 adopts a hardened tooth surface structure that is carburized, quenched and precision ground, and the worm wheel body 9 is made of zinc-based alloy or aluminum bronze. The input drive gear 3 and the input driven gear 2 are helical gears that are carburized, quenched and ground, thereby reducing meshing friction loss and improving load life and heat dissipation efficiency. The worm gear body 17 is carburized, quenched, and precision ground, resulting in a hardened tooth surface that is wear-resistant and has high transmission efficiency. The worm wheel body 9 is made of aluminum bronze / tin bronze or zinc-based alloy, with good mating friction pairs and resistance to scuffing and pitting. The helical gear 2 / 3 is carburized and ground to improve tooth profile accuracy and surface quality, reducing squealing. After comprehensive reshaping, the contact stress distribution is more uniform, the oil film bearing capacity on the tooth surface is improved, the temperature rise is reduced, and the overall efficiency and lifespan of the machine are improved simultaneously.

[0028] 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 invention (including the claims) is limited to these examples; within the framework of the 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 invention as described above, which are not provided in the details for the sake of brevity.

[0029] This invention 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 invention should be included within the scope of protection of this invention.

Claims

1. A high-efficiency heat-dissipating worm gear helical gear reducer motor for light-load machinery, characterized in that, include: The housing (10) has stepped holes for mounting bearings and end caps and external surface reinforcing ribs for external heat dissipation. Motor unit (1), which is fixedly connected to housing (10); The composite transmission mechanism includes a parallel shaft helical gear transmission stage installed in the input cavity of the housing (10) and a worm gear transmission pair installed in the output cavity of the housing (10), which is formed by the worm body (17) and the worm wheel body (9) meshing alternately. The parallel shaft helical gear transmission stage is used to realize the primary speed reduction and torque transmission of the motor unit (1), and the worm gear transmission pair further reduces the speed and outputs it to the output shaft (26). An axial positioning assembly is used to bear the radial / axial load generated by the transmission mechanism and to achieve axial positioning. The axial positioning assembly includes: tapered roller bearings (15) arranged at both ends of the worm body (17) and facing each other; a deep groove ball bearing (22) arranged on the output shaft (26); and a spacer ring (21), a shaft elastic retaining ring (19), and a hole elastic retaining ring (12) for axial limiting / positioning; it also includes a first adjusting shim (8) arranged between the end face of the worm gear body (9) and the axial support surface of the housing (10) and located near the viewing cover (7), the first adjusting shim (8) is used to adjust the worm gear-worm meshing clearance; and a second adjusting shim (14) arranged between the cover (11) and the outer ring of the tapered roller bearing (15), the second adjusting shim (14) is used to adjust the worm bearing preload; The lubrication and heat dissipation components are located in the lower oil sump and end cover area of ​​the housing (10) for splash lubrication and heat dissipation of the transmission pair and bearings; the sealing components are located at the input end cover and output end cover for sealing and isolating the motor input side and the extended end of the output shaft (26).

2. The high-efficiency heat-dissipating worm gear helical gear reducer motor for light-load machinery according to claim 1, characterized in that, The parallel shaft gear stage is a helical gear transmission, specifically including an input driving gear (3) set on the motor shaft and an input driven gear (2) meshing with the input driving gear (3); the staggered shaft transmission pair includes a worm gear and a worm body meshing with a worm body (17) and a worm wheel body (9), the input driven gear (2) and the worm body (17) are coaxially driven and connected, the worm body (17) is set along the transverse direction of the housing (10) and is supported at both ends of the housing (10) by tapered roller bearings; the worm wheel body (9) is set along the longitudinal direction of the housing (10) and is fixedly connected to the output shaft (26), its hub end face abuts against the axial support surface of the housing (10) through a first adjusting shim, thereby realizing the staggered arrangement and meshing transmission of the worm and the worm wheel in the output cavity of the housing (10).

3. The high-efficiency heat-dissipating worm gear helical gear reducer motor for light-load machinery according to claim 1, characterized in that, The worm body (17) is rotatably mounted in the symmetrical bearing seats of the housing (10) via tapered roller bearings (15) at both ends. The two tapered roller bearings (15) are arranged facing each other to withstand the bidirectional axial force generated by the meshing of the worm. The output shaft (26) is rotatably mounted in the output end bearing seat of the housing (10) via a deep groove ball bearing (22), and is axially limited by a spacer ring (21) and a shaft elastic retaining ring (19).

4. The high-efficiency heat-dissipating worm gear helical gear reducer motor for light-load machinery according to claim 2, characterized in that, The input passive gear (2) is engaged with the keyway on the journal of the worm body (17) through the keyway set in the inner hole of the gear, and is embedded between the two through the first ordinary flat key (18); the worm wheel body (9) is engaged with the keyway on the outer circle of the output shaft (26) through the keyway set in its inner hole, and is embedded between the two through the second ordinary flat key (25); the worm wheel-worm meshing clearance is adjusted by changing the thickness of the first adjusting shim (8) set between the end face of the worm wheel body (9) and the support surface of the housing (10); the worm bearing preload is adjusted by changing the thickness of the second adjusting shim (14) set between the cover (11) and the outer ring of the tapered roller bearing (15), and the first adjusting shim (8) and the second adjusting shim (14) are metal adjusting shims.

5. The high-efficiency heat-dissipating worm gear helical gear reducer motor for light-load machinery according to claim 1, characterized in that, The lubrication and heat dissipation assembly includes: An oil baffle ring (16) is provided adjacent to the worm body (17). The oil baffle ring (16) forms a guide edge along the circumference. During operation, it throws the oil towards the worm-worm wheel meshing area and the bearing areas on both sides. An oil return channel and / or spiral guide ribs are provided on the inner wall of the housing (10), and the channel guides the oil back to the bottom oil pool of the housing from the meshing area and the bearing area. The vent plug (6) located on the upper part of the housing (10) is used to balance the pressure inside and outside the housing (10) and suppress the leakage of oil mist caused by temperature rise; The sight glass cover (7) is installed on the side wall of the housing (10) and located at the normal oil level height for real-time observation of oil level and oil quality; The oil plug (20) located at the lowest point of the bottom of the housing (10) is used for draining oil and maintenance; The outer surface of the enclosure (10) is integrally formed with heat dissipation reinforcing ribs and / or sheet-like heat dissipation surfaces; Among them, the oil baffle ring (16), oil return channel, inner wall spiral guide rib, vent plug (6), sight glass cover (7) and oil plug (20) together define the partition structure of the upper air chamber and the lower oil chamber in space along the direction of gravity. During operation, the oil heats the tooth surface and bearing friction heat to the housing (10), and after heat dissipation through the outer surface, it flows back to the oil sump.

6. The high-efficiency heat-dissipating worm gear helical gear reducer motor for light-load machinery according to claim 5, characterized in that, The sealing assembly includes: The input side is a non-contact seal, which is formed by the cooperation of a cover (11) and a gasket (13). The gasket (13) is embedded between the cover (11) and the input shaft, and a multi-level annular gap labyrinth channel is defined at the input end of the housing (10). A set gap is maintained between the rotating surface of the input shaft end and the cover (11). The contact seal on the output side is formed by a double-lip oil seal (24) press-fitted into the stepped hole at the output end of the housing (10) or into the end hole of the cover (11). The double-lip oil seal (24) faces the oil cavity side and is sealed to the polished running surface of the output shaft (26). Among them, the elastic retaining ring (12) for the hole is located at the end steps of the input end and the output end of the housing (10) to axially limit the oil seal or end cover.

7. The high-efficiency heat-dissipating worm gear helical gear reducer motor for light-load machinery according to claim 5, characterized in that, The vent plug (6) is located on the upper surface of the housing (10) and is higher than the tooth tip circle of the worm gear body (9) in the vertical direction. The vent plug (6) is provided with an anti-oil return structure and a breathable one-way valve, and a replaceable oil mist collection core is provided in the ventilation path.

8. The high-efficiency heat-dissipating worm gear helical gear reducer motor for light-load machinery according to claim 5, characterized in that, The outer wall of the housing (10) facing the worm gear body (9) is provided with a thickened heat-conducting rib area. The inner side of the thickened heat-conducting rib area corresponds to the meshing area of ​​the worm gear body (9), and the outer side forms a sheet-like heat dissipation surface. The oil baffle ring (16) is set at a splash radius position that is larger than the pitch circle radius of the worm gear body (9), so that the splashed oil first covers the tooth surface of the worm body (17) and then falls back to the tooth surface of the worm gear body (9), so as to preferentially cool the high-heat area. The inner wall of the housing (10) forms a spiral guide rib along the axial direction of the worm body (17) that is consistent with the worm rotation direction, which is used to push the oil to the bearing areas at both ends.

9. The high-efficiency heat-dissipating worm gear helical gear reducer motor for light-load machinery according to claim 2, characterized in that, The worm gear body (17) adopts a hardened tooth surface structure with carburizing and quenching and fine grinding, the worm wheel body (9) adopts zinc-based alloy or aluminum bronze material, and the input driving gear (3) and the input driven gear (2) adopt helical gears with carburizing and quenching and grinding.

10. The high-efficiency heat-dissipating worm gear helical gear reducer motor for light-load machinery according to claim 6, characterized in that, A replaceable thin-walled bushing is provided at the output side seal as the running surface of the double-lip oil seal (24). The outer circle of the bushing forms multiple running areas that can be used in a staggered manner along the circumferential direction. During maintenance, the sealing surface can be updated by rotating or replacing the bushing. In addition, under different installation postures, the above-mentioned lubrication and sealing components still maintain the partitioned structure of the upper air chamber and the lower oil chamber to ensure stable oil level and low leakage.

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