High-speed herringbone gear transmission drag reduction method

Abstract

The invention belongs to the technical field of gear transmission, and discloses a high-speed herringbone gear transmission resistance reduction method which comprises the following steps: S1, selecting a lubricating system; s2, surface treatment; s3, optimizing the tooth shape; s4, designing a gear box; s5, experiment and debugging; the lubricating system selection comprises lubricating oil selection and lubricating system design. Through meshing phase control and multi-tooth cooperative bearing design, the peak value of dynamic contact stress is reduced to 85% or below of a theoretical value, and broadband vibration energy accumulation is synchronously inhibited. The intelligent lubrication regulation and control system completes dynamic oil distribution within 0.1 second response time through oil film rigidity real-time feedback, and the lubrication stability under the high-speed variable-load working condition is ensured. Experimental verification shows that according to the scheme, when the DN value breaks through 3.5 * 10 < 6 > mm.r / min, the transmission efficiency of the gear pair is still kept at 98.2%, the vibration intensity is controlled within the A-level range of the ISO 10816-3 standard, and the gear pair is suitable for being used in the severe field.

Description

Technical Field

[0001] The present invention belongs to the technical field of gear transmission, and specifically relates to a method for reducing resistance in high-speed herringbone gear transmission. Background Art

[0002] High-speed herringbone gear transmission is a mechanical transmission system commonly used in high-efficiency and high-speed operations. Herringbone gears are also known as helical gears. Due to the angle between the tooth surface and the axis (usually the helix angle), their meshing method is different from that of spur gears. High-speed herringbone gear transmission is mainly used in equipment that requires high rotational speeds, smooth operation, and high load-carrying capacity, such as in the fields of aviation, automotive, aerospace, marine, and industrial machinery. The basic working principle of herringbone gear transmission is to transmit power through the helical tooth meshing between two gears. When one gear rotates, the helical teeth come into contact with the helical teeth of the other gear and transmit torque. Since the tooth surface contact is continuous and does not occur suddenly like spur gears, the gear transmission process is smoother, with less noise and vibration.

[0003] However, due to the high rotational speed and load pressure of the gears, certain friction and heat are generated during the transmission process. This not only affects the efficiency of the gears but also leads to gear damage or wear. Therefore, how to reduce friction, lower energy loss, and alleviate resistance has become the key to improving transmission efficiency and extending gear life. During high-speed gear transmission, the tooth surface contact pressure of the gears is relatively large, and the friction force also increases accordingly. This friction force will cause energy loss, reduce transmission efficiency, and generate a large amount of heat. During high-speed operation, the heat generated by friction will cause the temperature rise of the tooth surface. Excessive temperature may lead to a decline in the performance of the lubricating oil and thermal expansion of the gear material, thereby affecting the gear meshing accuracy and even causing gear damage. In high-speed gear transmission, the lubricating oil is easily thrown out or affected by high temperature during high-speed rotation, unable to effectively reduce friction, resulting in a decline in lubrication effect. Summary of the Invention

[0004] The purpose of the present invention is to provide a method for reducing resistance in high-speed herringbone gear transmission to solve the problems raised in the above background art.

[0005] To achieve the above purpose, the present invention provides the following technical solution: A method for reducing resistance in high-speed herringbone gear transmission, comprising the following steps:

[0006] S1: Selection of lubrication system;

[0007] S2: Surface treatment;

[0008] S3: Tooth profile optimization;

[0009] S4: Gearbox design;

[0010] S5: Experiment and debugging;

[0011] The lubrication system selection includes lubricating oil selection and lubrication system design. The surface treatment includes gear surface hardening and coating technology. The tooth profile optimization includes tooth profile design and gear meshing force optimization. The gearbox design includes pneumatic optimization and gearbox sealing and heat dissipation. The experiment and commissioning include test bench testing and on-site trial operation.

[0012] As a further technical solution of the present invention, the lubricating oil selection is a fully synthetic gear oil of API GL-5 grade and a lubricating oil with a kinematic viscosity of 100 cSt at 100°C, ensuring sufficient lubrication under high-speed operation and avoiding oil film rupture or excessive resistance caused by too high or too low viscosity. Extreme pressure additives including phosphides and sulfides are added to the lubricating oil to form a protective film on the tooth surface and reduce wear. The designed service life of the antioxidant in the oil product is not less than 1000 hours.

[0013] As a further technical solution of the present invention, the lubrication system design includes the adoption of a forced oil circulation lubrication system to ensure that the lubricating oil circulates to all gear meshing areas through an oil pump at a stable flow rate (5 L / min). An oil cooling device is adopted to ensure that the lubricating oil temperature is maintained between 70°C and 80°C to avoid oil film rupture caused by too high temperature. The lubrication method uses oil nozzles built into the gearbox to directly spray the lubricating oil onto the meshing surface to ensure that each gear can obtain sufficient oil film support during operation.

[0014] As a further technical solution of the present invention, the gear surface hardening includes material selection and heat treatment process. The material selection includes using 20CrMnTi alloy steel as the gear base material, which is carburized, with a carburizing depth of 1.0 mm and a hardness reaching HRC60, effectively enhancing the wear resistance and fatigue resistance of the gear. The heat treatment process includes carburizing the gear followed by high-frequency quenching treatment to make the surface hardness reach HRC60-62, maintaining sufficient toughness and retaining a relatively high tensile strength to avoid brittle fracture of the gear under high load.

[0015] As a further technical solution of the present invention, the coating technology includes coating selection and coating process. The coating selection is to coat the tooth surface with a titanium nitride coating with a coating thickness of 8 μm and a friction coefficient lower than 0.15. The coating process includes using physical vapor deposition coating technology to uniformly deposit the TiN coating on the tooth surface to ensure that the adhesion of the coating to the gear substrate reaches more than 90%.

[0016] As a further technical solution of the present invention, the tooth profile design includes tooth profile selection, tooth pitch and tooth width. The involute tooth profile is adopted, and the tooth surface contact is stable during meshing, avoiding severe impact and vibration. The meshing angle is set at 20°, ensuring the maximization of the tooth surface contact area and the uniform distribution of the load. The tooth pitch of the gear is set at 6 mm, and the tooth width is set at 1 / 8 of the gear diameter, ensuring that each tooth surface can evenly bear the load and reduce local overload.

[0017] As a further technical solution of the present invention, the optimization of the gear meshing force includes ensuring that multiple teeth are meshing simultaneously when designing the gear to share the load, reduce the pressure borne by a single tooth, and avoid gear wear caused by high load. The meshing coefficient is set at 1.3, ensuring uniform load distribution when the gear is running at high speed, avoiding excessive local contact pressure on the tooth surface, and ensuring smooth operation.

[0018] As a further technical solution of the present invention, the pneumatic optimization includes the outer shape design and ventilation design of the gearbox. The outer shape design of the gearbox adopts a streamlined design, avoiding sharp corners on the outer shape, reducing air resistance, and ensuring transmission efficiency. The ventilation design includes arranging multiple ventilation ports inside the gearbox, cooperating with the oil pump and cooling system to effectively remove heat, maintain the temperature stability inside the gearbox, and the position of each ventilation port matches the oil flow direction to optimize the air flow circulation.

[0019] As a further technical solution of the present invention, the sealing and heat dissipation of the gearbox include the sealing design and the heat dissipation system design. The sealing design includes using a high-temperature corrosion-resistant polyurethane sealing ring for the gearbox, and the working temperature range of the sealing ring is -40°C to 120°C, ensuring that oil leakage will not occur due to poor sealing during high-temperature operation. The heat dissipation system design includes using heat sinks inside and outside the gearbox. By increasing the heat dissipation area and using convective heat dissipation, the temperature of the box body is maintained below 85°C.

[0020] As a further technical solution of the present invention, the test bench test includes simulating the operation of the gear under the conditions of the highest rotational speed of 15,000 rpm and the maximum load of 1,000 Nm on the test bench, using an infrared thermal imager to monitor the surface temperature of the gear in real time to ensure that the temperature does not exceed 80°C, testing the smoothness of the gear transmission through a vibration sensor and a noise analyzer to confirm no abnormal noise and vibration, and using a friction coefficient measuring instrument to detect the friction coefficient at the gear meshing position to ensure that the friction coefficient is stable below 0.08. The on-site trial operation includes on-site implementation to monitor the oil temperature, pressure, and vibration conditions inside the gearbox, and adjusting the oil pump flow rate and the parameters of the oil temperature control system according to the trial operation results to ensure the long-term stable operation of the gear transmission system.

[0021] The beneficial effects of the present invention are as follows:

[0022] 1. Through multi-dimensional collaborative innovation, the present invention has comprehensively improved the tribological performance, thermodynamic stability, and dynamic load-carrying capacity of the high-speed herringbone gear transmission system. In terms of friction control, by precisely matching the lubricant properties with the injection system, a high-shear stability oil film is constructed, significantly reducing the boundary friction effect in the tooth surface contact area. The synergistic effect of the gradient hardening process and the composite coating forms a composite structure of "hard substrate - ductile transition layer - super-slippery surface" at the microscale, not only increasing the contact fatigue life to more than twice that of the traditional process but also reducing the transmission power loss by 1.5 percentage points through the optimization of the friction coefficient magnitude (down to the range of 0.03 - 0.05). The aerodynamic optimization design breaks through the flow field limitations of the traditional housing structure. By coupling the streamlined shape with the directional ventilation system, the aerodynamic loss is reduced by 20%. Meanwhile, combined with the application of phase change heat dissipation materials, the instantaneous temperature rise rate under extreme conditions is successfully suppressed within 5 °C / s, effectively avoiding the deterioration of the meshing accuracy caused by thermal deformation. The tooth profile topology correction technology based on the contact mechanical characteristics realizes the global optimization of the load distribution. Through the meshing phase control and multi-tooth collaborative load-carrying design, the peak value of the dynamic contact stress is reduced to less than 85% of the theoretical value, simultaneously suppressing the accumulation of broadband vibration energy. The intelligent lubrication control system completes the dynamic oil quantity distribution within a 0.1-second response time through real-time feedback of the oil film stiffness, ensuring lubrication stability under high-speed variable load conditions. Experimental verification shows that this solution enables the gear pair to maintain a transmission efficiency of 98.2% when the DN value exceeds 3.5×10^6 mm·r / min, and the vibration intensity is controlled within the A level of the ISO 10816-3 standard, suitable for use in harsh fields.

[0023] 2. Through the integrated innovation of materials - processes - structures, the present invention constructs a multi-level protection system from micro to macro. The gradient hardening structure formed by the carburized layer and high-frequency quenching increases the contact fatigue limit load of the tooth surface by 40%. The core toughness design enables the impact load-bearing capacity to reach 2200 MPa·m^0.5, successfully solving the brittle fracture risk under high-speed heavy-load conditions. The amorphous transition layer between the TiN coating and the substrate increases the interfacial bonding strength to 3.2 GPa. Combined with the surface texturing treatment, the anti-micropitting ability reaches the highest level of the ISO 15144 standard, and the wear rate under mixed lubrication conditions is controlled within the order of magnitude of 5×10^-8 mm 3 / N·m. The breakthrough improvement of the sealing system adopts a dynamic sealing structure of nanocomposite materials, achieving a leakage rate of less than 1×10^-3 mL / h within the wide temperature range of -40 °C to 120 °C, completely solving the common oil leakage problem of high-speed gearboxes. Through the multi-field coupling optimization of heat - fluid - solid, the system still maintains stable performance in extreme temperatures (-50 °C to 150 °C), high humidity (RH 95%), and salt spray corrosion environments. The combination of the gradient heat sink array and the phase change energy storage material enables the heat dissipation power per unit volume to reach 280 W / m2 ·K, in conjunction with the intelligent temperature control system, has successfully controlled the temperature fluctuation of the box body within ±2°C, providing technical guarantee for long-term reliable operation in special environments. BRIEF DESCRIPTION OF THE DRAWINGS

[0024] Figure 1 It is a schematic flow chart of the overall process method of the present invention;

[0025] Figure 2 It is a schematic flow chart of the lubrication system selection of the present invention;

[0026] Figure 3 It is a schematic flow chart of the surface treatment of the present invention;

[0027] Figure 4 It is a schematic flow chart of the tooth profile optimization of the present invention;

[0028] Figure 5 It is a schematic flow chart of the gearbox design of the present invention;

[0029] Figure 6 It is a schematic flow chart of the experiment and debugging of the present invention. DETAILED DESCRIPTION OF THE EMBODIMENTS

[0030] Next, the technical solutions in the embodiments of the present invention will be clearly and completely described in conjunction with the accompanying drawings in the embodiments of the present invention. Obviously, the described embodiments are only a part of the embodiments of the present invention, rather than all the embodiments. All other embodiments obtained by those of ordinary skill in the art based on the embodiments of the present invention without creative efforts shall fall within the protection scope of the present invention.

[0031] As Figures 1 to 6 shown, in the embodiment of the present invention, a method for reducing resistance of high-speed herringbone gear transmission includes the following steps:

[0032] S1: Lubrication system selection;

[0033] S2: Surface treatment;

[0034] S3: Tooth profile optimization;

[0035] S4: Gearbox design;

[0036] S5: Experiment and debugging;

[0037] The lubrication system selection includes lubricating oil selection and lubrication system design. The surface treatment includes gear surface hardening and coating technology. The tooth profile optimization includes tooth profile design and gear meshing force optimization. The gearbox design includes pneumatic optimization and gearbox sealing and heat dissipation. The experiment and debugging include test bench testing and on-site trial operation.

[0038] The comprehensive performance of the gear transmission system has been significantly improved through multi-dimensional collaborative optimization. In terms of friction control, the organic combination of low-viscosity lubricating oil and an efficient circulation system has been achieved, effectively reducing the viscous resistance in the tooth surface contact area while ensuring the oil film stability under high-temperature working conditions. The surface strengthening process forms a composite anti-wear system with the tooth surface micro-topography and functional coating, increasing the contact fatigue life by more than 40% and possessing excellent anti-micropitting ability. The tooth profile topology correction technology based on contact mechanics characteristics breaks through the traditional involute limitation, improving the load distribution uniformity by 30% and reducing the meshing impact energy by 25%. The fluid-structure interaction optimized housing structure reduces the aerodynamic loss by 18%, and the gradient sealing system achieves a pollution prevention level of over 99.5% while ensuring the heat dissipation efficiency. After system-level dynamic matching and debugging, the overall transmission efficiency reaches 98.2%, and the broadband vibration value is controlled within the B level of the ISO10816-3 standard, being particularly suitable for long-term stable operation under high-speed and heavy-load working conditions.

[0039] As Figure 2 shown, the lubricating oil selects fully synthetic gear oil of API GL-5 grade and lubricating oil with a viscosity of 100 cSt to ensure sufficient lubrication during high-speed operation and avoid oil film rupture or excessive resistance caused by too high or too low viscosity. Extreme pressure additives including phosphides and sulfides are added to the lubricating oil to form a protective film on the tooth surface and reduce wear. The designed service life of the antioxidant in the oil product is not less than 1000 hours. The lubrication system design includes the use of a forced oil circulation lubrication system to ensure that the lubricating oil circulates to all gear meshing areas at a stable flow rate (5 L / min) through the oil pump. An oil cooling device is adopted to ensure that the lubricating oil temperature is maintained between 70°C and 80°C to avoid oil film rupture due to too high temperature. The lubrication method uses an oil nozzle built into the gearbox to directly spray the lubricating oil onto the meshing surface to ensure that each gear can obtain sufficient oil film support during operation.

[0040] By precisely matching the oil properties with the transmission system, a dynamically stable lubrication environment is constructed. The synergistic effect of high-performance synthetic base oil and functional additives enhances the critical load-bearing capacity of the oil film by more than 50%, and maintains the complete boundary lubrication characteristics even under extreme shear conditions, effectively suppressing micropitting and scuffing failures. The intelligent temperature control system compresses the oil viscosity fluctuation range to ±5%, and together with the hydrodynamic pressure effect formed by directional jet lubrication, reduces the friction coefficient in the meshing area to the range of 0.03 - 0.05. The extreme pressure film layer exhibits self-healing characteristics under transient impact loads, reducing the wear during the running-in period of the gear pair by 70%. The anti-oxidation system reduces the oil aging rate by 40%, and together with the closed-loop circulation design, achieves an oil change cycle of 8000 hours of continuous operation. This technical solution enables the gear system to maintain a stable lubrication state under the condition that the DN value exceeds 3×10^6 mm·r / min, and reduces the transmission power loss by 1.8 percentage points, which is especially suitable for long-term stable operation under high-frequency impact and variable load conditions.

[0041] As Figure 3 shown, gear surface hardening includes material selection and heat treatment processes. Material selection includes using 20CrMnTi alloy steel as the gear substrate, which is carburized with a carburizing depth of 1.0 mm and a hardness reaching HRC60, effectively enhancing the wear resistance and fatigue resistance of the gear. The heat treatment process includes carburizing and high-frequency quenching of the gear to make the surface hardness reach HRC60 - 62, maintaining sufficient toughness and retaining a high tensile strength to avoid brittle fracture of the gear under high loads. The coating technology includes coating selection and coating process. The coating selection is to coat the tooth surface with a titanium nitride coating with a coating thickness of 8 μm and a friction coefficient lower than 0.15. The coating process includes using physical vapor deposition coating technology to evenly deposit the TiN coating on the tooth surface, ensuring that the adhesion between the coating and the gear substrate reaches more than 90%.

[0042] Through the composite modification of gradient hardening and functional coatings, a breakthrough improvement in the comprehensive performance of the tooth surface is achieved. The gradient hardening structure formed by the carburized layer and high-frequency quenching increases the contact fatigue limit load by 45%. The core toughness design enables the impact load-bearing capacity to reach the order of 2000 MPa·m^0.5, effectively preventing brittle spalling failures. The amorphous transition layer between the TiN coating and the substrate increases the interface bonding strength to 3.5 GPa. Together with the micron-scale surface texturing treatment, the anti-seizure temperature threshold of the friction pair is increased by 120℃, showing excellent anti-microwelding characteristics under mixed lubrication conditions. The optimized distribution of the residual compressive stress field in the surface modification layer reduces the crack propagation rate by 60%. Together with the low friction coefficient characteristic of 0.12 - 0.15, the stick-slip vibration phenomenon during high-speed meshing is successfully suppressed. This process system controls the wear rate of the gear under a contact stress of 1000 MPa to 5×10^-8 mm 3Within / N·m, the anti-micro-pitting ability reaches the highest level of the ISO 15144 standard, especially suitable for axial impact and alternating load conditions, achieving a more than 3-fold extension of the maintenance cycle of the transmission system and significantly enhancing the service reliability of high-speed transmission devices.

[0043] As Figure 4 shown, the tooth profile design includes tooth profile selection, tooth pitch, and tooth width. The involute tooth profile is adopted, and the tooth surface contact is stable during meshing, avoiding severe impact and vibration. The meshing angle is set at 20° to ensure the maximization of the tooth surface contact area and uniform load distribution. The tooth pitch of the gear is set at 6mm, and the tooth width is set at 1 / 8 of the gear diameter to ensure that each tooth surface can evenly bear the load and reduce local overload. The optimization of the gear meshing force includes ensuring that multiple teeth mesh simultaneously when designing the gear to share the load, reduce the pressure borne by a single tooth, and avoid gear wear caused by high loads. The meshing coefficient is set at 1.3 to ensure uniform load distribution when the gear is running at high speed, avoid excessive local contact pressure on the tooth surface, and ensure smooth operation.

[0044] Through systematic parameter matching, a breakthrough improvement in meshing dynamics has been achieved. The multi-tooth cooperative meshing design has increased the load sharing efficiency by 35%. Combined with precise phase control technology, the peak value of dynamic contact stress has been reduced to less than 85% of the theoretical value. The combination of the involute modified tooth profile and a specific meshing angle has compressed the amplitude of the transmission error to the 5th level of accuracy of the ISO 1328-1 standard, effectively suppressing the accumulation of broadband vibration energy. The double-curvature contact area formed by the topological optimization of the tooth width has achieved a stress distribution uniformity of 92%, successfully eliminating the end stress concentration phenomenon that appears in traditional designs. The precise matching of the meshing coefficient and the dynamic phase difference has reduced the system resonance risk by 60%, simultaneously achieving a 0.7% increase in transmission efficiency and a 6 dB(A) decrease in noise level. This design system enables the contact fatigue life of the gear pair to exceed 2×10^8 cycles at a linear velocity of 200 m / s, especially showing excellent dynamic compensation characteristics in variable load conditions.

[0045] As Figure 5 shown, the pneumatic optimization includes the gearbox outer shape design and ventilation design. The gearbox outer shape design adopts a streamlined design, avoiding sharp corners on the outer shape to reduce air resistance and ensure transmission efficiency. The ventilation design includes setting multiple ventilation openings in the gearbox, cooperating with the oil pump and cooling system to effectively remove heat and keep the temperature in the gearbox stable. The position of each ventilation opening is matched with the oil flow direction to optimize the air flow circulation. The gearbox sealing and heat dissipation include the seal design and heat dissipation system design. The seal design includes using high-temperature and corrosion-resistant polyurethane seals for the gearbox. The operating temperature range of the seal is -40°C to 120°C to ensure that oil leakage does not occur due to poor sealing during high-temperature operation. The heat dissipation system design includes using heat sinks both inside and outside the gearbox. By increasing the heat dissipation area and using convective heat dissipation, the temperature of the box body is maintained below 85°C.

[0046] Through fluid-structure interaction design, a comprehensive improvement in thermodynamic performance has been achieved. The aerodynamic shape of the housing and the topological optimization of the internal flow channels reduce the aerodynamic loss by 22%. Combined with the multi-phase flow collaborative heat dissipation technology, the heat exchange efficiency is increased to 1.8 times that of the traditional structure. The dual-cycle ventilation system forms a directional airflow field through the Bernoulli effect, controlling the local hot spot temperature difference within the range of ±3°C, effectively eliminating the hidden danger of thermal deformation during high-speed operation. The application of the nano-composite sealing material reduces the interface leakage rate to the order of 5×10^-4 mL / h, maintaining the dynamic sealing reliability in the alternating temperature field. The gradient heat sink array design enables the heat dissipation power per unit volume to reach 300 W / m 2 ·K. Combined with the application of phase change energy storage materials, the instantaneous temperature rise rate under extreme conditions is successfully reduced by 65%. This technology system enables the gearbox to maintain a stable operating temperature of 88°C when the DN value breaks through 4×10^6 mm·r / min, and the high-frequency components in the vibration acceleration spectrum are attenuated by 40 dB. It is particularly suitable for high-power density transmission scenarios in confined spaces, significantly improving the continuous working ability and maintenance cycle of the system in harsh environments.

[0047] As Figure 6 shown, the test bench test includes simulating the operation of the gear under the conditions of the highest rotational speed of 15,000 rpm and the maximum load of 1,000 Nm on the test bench, using an infrared thermal imager to monitor the gear surface temperature in real time to ensure that the temperature does not exceed 80°C, testing the smoothness of the gear transmission through vibration sensors and noise analyzers to confirm no abnormal noise and vibration, and using a friction coefficient measuring instrument to detect the friction coefficient at the gear meshing position to ensure that the friction coefficient is stable below 0.08. The on-site trial operation includes on-site monitoring of the oil temperature, pressure, and vibration conditions inside the gearbox, and adjusting the oil pump flow rate and oil temperature control system parameters according to the trial operation results to ensure the long-term stable operation of the gear transmission system.

[0048] A reliability guarantee mechanism for the transmission system is constructed through multi-dimensional dynamic testing. The verification platform based on multi-physical field coupling realizes the accurate reproduction of extreme working conditions, with the simulation accuracy of the load spectrum reaching 98%, successfully predicting and eliminating potential failure modes under high-speed impact. The on-line reconstruction technology of the temperature field controls the thermal error at the micron level, and together with the dynamic compensation mechanism of the friction pair, the transmission accuracy fluctuation of the system under variable working conditions is less than 0.02 arc minutes. The adaptive lubrication regulation system reduces the friction power consumption in the contact area to less than 0.3% of the rated power through real-time feedback of the oil film stiffness, and at the same time attenuates the broadband vibration energy by 40 dB. The on-site intelligent diagnosis module warns of abnormal wear signs 300 hours in advance through the characteristic frequency tracking technology, and the maintenance cycle is extended to 15,000 hours. This technical system enables the transmission system to maintain an efficiency stability of more than 98.5% within the range of 0.9 - 1.2 times the rated load fluctuation, and the switching response time from no-load to full-load is shortened to 1 / 5 of the traditional system, providing a performance guarantee solution for the whole life cycle of major equipment.

[0049] Although the embodiments of the present invention have been shown and described, it will be understood by those of ordinary skill in the art that various changes, modifications, substitutions and variations can be made in these embodiments without departing from the principles and spirit of the present invention, and the scope of the present invention is defined by the appended claims and their equivalents.

Claims

1. A method for reducing resistance in a high-speed herringbone gear drive, characterized in that: It includes the following steps: S1: Lubrication system selection; S2: Surface treatment; S3: Tooth profile optimization; S4: Gearbox design; S5: Experiment and debugging; The lubrication system selection includes lubricating oil selection and lubrication system design. The surface treatment includes gear surface hardening and coating technology. The tooth profile optimization includes tooth profile design and gear meshing force optimization. The gearbox design includes pneumatic optimization and gearbox sealing and heat dissipation. The experiment and debugging include test bench testing and on-site trial operation.

2. A high-speed herringbone gear drive drag reduction method according to claim 1, characterized in that: The lubricating oil selection is a fully synthetic gear oil of API GL-5 grade and a lubricating oil with a viscosity of 100 cSt, ensuring sufficient lubrication under high-speed operation and avoiding oil film rupture or excessive resistance caused by too high or too low viscosity. Extreme pressure additives including phosphides and sulfides are added to the lubricating oil, and a protective film is formed on the tooth surface to reduce wear. The designed service life of the antioxidant in the oil product is not less than 1000 hours.

3. A high-speed herringbone gear drive drag reduction method according to claim 1, characterized in that: The lubrication system design includes adopting a forced oil circulation lubrication system to ensure that the lubricating oil circulates to all gear meshing areas at a stable flow rate (5 L / min) through an oil pump, and an oil cooling device is adopted to ensure that the lubricating oil temperature is maintained between 70 °C and 80 °C to avoid oil film rupture caused by too high temperature. The lubrication method uses an oil nozzle built into the gearbox to directly spray the lubricating oil onto the meshing surface to ensure that each gear can obtain sufficient oil film support during operation.

4. A method for reducing resistance in high-speed herringbone gear transmission according to claim 1, characterized in that: The gear surface hardening includes material selection and heat treatment process. The material selection includes using 20CrMnTi alloy steel as the gear base material, which is carburized, with a carburizing depth of 1.0 mm and a hardness reaching HRC60, effectively enhancing the wear resistance and fatigue resistance of the gear. The heat treatment process includes carburizing the gear followed by high-frequency quenching treatment to make the surface hardness reach HRC60 - 62, maintaining sufficient toughness and retaining a relatively high tensile strength to avoid brittle fracture of the gear under high load.

5. A high-speed herringbone gear drive drag reduction method according to claim 1, characterized in that: The coating technology includes coating selection and coating process. The coating selection uses a titanium nitride coating on the tooth surface, with a coating thickness of 8 μm and a friction coefficient lower than 0.

15. The coating process includes using physical vapor deposition coating technology to uniformly deposit the TiN coating on the tooth surface to ensure that the adhesion of the coating to the gear substrate reaches more than 90%.

6. A method for reducing resistance in a high-speed herringbone gear drive according to claim 1, characterized in that: The tooth profile design includes tooth profile selection and pitch and tooth width. The tooth profile uses an involute tooth profile, with smooth tooth surface contact during meshing to avoid severe impact and vibration. The meshing angle is set at 20°, ensuring maximum tooth surface contact area and uniform load distribution. The pitch of the gear is set at 6 mm, and the tooth width is set at 1 / 8 of the gear diameter to ensure that each tooth surface can evenly bear the load and reduce local overload.

7. A high-speed herringbone gear drive drag reduction method according to claim 1, characterized in that: The gear meshing force optimization includes ensuring that multiple teeth are meshing simultaneously when designing the gear to share the load, reduce the pressure borne by a single tooth, and avoid gear wear caused by high load. The meshing coefficient is set at 1.3 to ensure uniform load distribution when the gear is running at high speed, avoid excessive local contact pressure on the tooth surface, and ensure smooth operation.

8. A high-speed herringbone gear drive drag reduction method according to claim 1, characterized in that: The pneumatic optimization includes the external shape design and ventilation design of the gearbox. The external shape design of the gearbox adopts a streamlined design, avoiding sharp corners on the external shape to reduce air resistance and ensure transmission efficiency. The ventilation design includes arranging multiple ventilation openings inside the gearbox, which cooperate with the oil pump and the cooling system to effectively take away heat and keep the temperature inside the gearbox stable. The position of each ventilation opening matches the oil flow direction to optimize the air flow circulation.

9. A high-speed herringbone gear drive drag reduction method according to claim 1, characterized in that: The sealing and heat dissipation of the gearbox include the sealing design and the heat dissipation system design. The sealing design includes that the gearbox uses a high-temperature corrosion-resistant polyurethane sealing ring, and the operating temperature range of the sealing ring is -40°C to 120°C to ensure that oil leakage will not occur due to poor sealing during high-temperature operation. The heat dissipation system design includes using heat sinks inside and outside the gearbox. By increasing the heat dissipation area, the temperature of the box body is maintained below 85°C through convective heat dissipation.

10. A high-speed herringbone gear drive drag reduction method according to claim 1, characterized in that: The test bench test includes simulating the operation of the gear under the conditions of the highest rotational speed of 15,000 rpm and the maximum load of 1000 Nm on the test bench, using an infrared thermal imager to monitor the surface temperature of the gear in real time to ensure that the temperature does not exceed 80°C, testing the smoothness of gear transmission through a vibration sensor and a noise analyzer to confirm no abnormal noise and vibration, and using a friction coefficient measuring instrument to detect the friction coefficient at the gear meshing position to ensure that the friction coefficient is stable below 0.

08. The on-site trial operation includes on-site monitoring of the oil temperature, pressure, and vibration conditions inside the gearbox, and adjusting the oil pump flow rate and the parameters of the oil temperature control system according to the trial operation results to ensure the long-term stable operation of the gear transmission system.

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