Variable stiffness gear assembly, debugging method and transmission device

Abstract

The invention discloses a variable stiffness gear assembly, a debugging method and a transmission device, and relates to the technical field of high-speed heavy-duty gear transmission devices.The variable stiffness gear assembly comprises a gear shaft with a through hole formed in the axis position and an output shaft coaxially arranged in the through hole, and an annular cavity is formed between the inner side wall of the gear shaft and the outer side wall of the output shaft; one end of the annular cavity is sealed through an inner gear sleeve internally provided with an inner spline, the inner gear sleeve is fixedly connected with one end of the gear shaft, and the other end of the annular cavity is sealed through an arc-shaped cushion block located between the inner side wall of the gear shaft and the outer side wall of the output shaft. The shaft end of the output shaft extends into the inner gear sleeve and is in meshing transmission with the inner spline of the inner gear sleeve through the outer spline. The gear shaft is provided with a feeding channel used for injecting filler into the annular cavity, and the end of the feeding channel is sealed through a plugging piece. The impact load resistance of the low-speed gear assembly is improved, the mass of the low-speed gear assembly is reduced, the supporting rigidity of the low-speed gear assembly is changed, and then the service performance of the gear transmission device is improved.

Description

Technical Field

[0001] This invention relates to the field of high-speed heavy-duty gear transmission technology, specifically a variable stiffness gear assembly, debugging method, and transmission device. Background Technology

[0002] In the field of industrial turbines, especially in generator sets driven by gas turbines and steam turbines, high-speed, heavy-duty gear transmissions serve as key components connecting the power source and the generator, undertaking the core functions of power transmission and speed conversion. These high-speed, heavy-duty gear transmissions operate at relatively high power ratings, typically tens of megawatts or even up to 100 MW. However, structurally, these transmissions often employ a single-stage transmission design and are characterized by the large mass of low-speed gear components. Furthermore, the service conditions for these transmissions are extremely demanding, requiring a certain capacity to withstand impact loads. These stringent service conditions place extremely high demands on the overall performance of the transmission.

[0003] Currently, gear transmission devices are prone to increased vibration and difficulty in effectively mitigating impact loads when dealing with frequent starts and stops and sudden loads, which in turn affects the reliability and service life of the gear transmission device. Summary of the Invention

[0004] The purpose of this invention is to provide a variable stiffness gear assembly and its debugging method, which improves the impact load resistance of the low-speed gear assembly, reduces the mass of the low-speed gear assembly, and changes its support stiffness, thereby improving the service performance of the gear transmission device.

[0005] To achieve the above objectives, the specific solution adopted by the present invention is as follows: a variable stiffness gear assembly, comprising a gear shaft with a through hole at its axial center and an output shaft coaxially disposed within the through hole, wherein an annular cavity is formed between the inner wall of the gear shaft and the outer wall of the output shaft, one end of the annular cavity is sealed by an inner gear sleeve having internal splines, and the inner gear sleeve is fixedly connected to one end of the gear shaft, and the other end of the annular cavity is sealed by an arc-shaped pad located between the inner wall of the gear shaft and the outer wall of the output shaft; the shaft end of the output shaft extends into the inner gear sleeve and engages with the inner splines of the inner gear sleeve through an external spline for transmission; a feed channel for injecting filler into the annular cavity is provided on the gear shaft, and the end of the feed channel is sealed by a sealing member.

[0006] As an optimized solution for the aforementioned variable stiffness gear assembly: the end of the inner gear sleeve facing away from the gear shaft is fixedly provided with a protrusion extending toward the center of the inner gear sleeve, and the end face of the output shaft extending into the inner gear sleeve abuts against the protrusion.

[0007] As another optimization of the above-mentioned variable stiffness gear assembly: the output shaft is a stepped shaft, and the output shaft has a variable diameter section near both ends of the annular cavity. A sealing ring is provided between the outer wall of the variable diameter section and the inner wall of the gear shaft for sealing.

[0008] As another optimization of the above-mentioned variable stiffness gear assembly: the end of the gear shaft away from the inner gear sleeve has a notch, and the inner sidewall of the notch and the outer sidewall of the output shaft form an extended mounting area for installing the arc-shaped pad.

[0009] As another optimization of the above-mentioned variable stiffness gear assembly: the output shaft has several protrusions distributed along its axial direction on the outer wall of the annular cavity.

[0010] As another optimization of the aforementioned variable stiffness gear assembly, the filler is high-viscosity lubricating oil.

[0011] As another optimization scheme for the aforementioned variable stiffness gear assembly: the high viscosity lubricating oil contains 10-40% by mass of a mixed additive, which, according to the mass ratio, consists of 4-8 parts of organic bentonite, 12-16 parts of paraffin wax, 3-5 parts of modified graphite, 3-6 parts of modified molybdenum disulfide, and 1.6-4 parts of a polar activator, wherein the polar activator is a mixture of methanol and water in a 1:1 volume ratio.

[0012] A method for debugging the variable stiffness gear assembly as described above involves driving the variable stiffness gear assembly to rotate at its operating speed, using a first circular runout detector and a second circular runout detector to simultaneously detect the mechanical runout of the gear shaft and the output shaft, using the data detected by the first circular runout detector as a reference, adjusting the shims to adjust the center position of the output shaft until the difference between the data detected by the second circular runout detector and the data detected by the first circular runout detector is less than a preset value.

[0013] A high-speed heavy-duty gear transmission device includes a housing, in which a high-speed gear assembly and a low-speed gear assembly are disposed and meshed, wherein the low-speed gear assembly is the aforementioned variable stiffness gear assembly.

[0014] A high-speed heavy-duty gear transmission device includes a housing, in which a high-speed gear assembly and a low-speed gear assembly are disposed, wherein the low-speed gear assembly is the aforementioned variable stiffness gear assembly.

[0015] As an optimized solution for the aforementioned high-speed heavy-duty gear transmission device: the high-speed gear assembly includes an input shaft and a high-speed transmission gear fixedly sleeved on the input shaft, and the input shaft is rotatably connected to the housing through a sliding bearing; the gear shaft is rotatably connected to the housing through a sliding bearing, and both ends of the gear shaft extend out of the housing.

[0016] Compared with the prior art, the present invention has the following beneficial effects: 1. This invention provides a variable stiffness gear assembly. An inner gear sleeve is fixedly mounted at one end of the gear shaft, and the end of the output shaft extends into and is fixedly connected to the inner gear sleeve. This extends the power transmission path of the gear assembly, allowing for a larger allowable torsional angle under the same torsional deformation requirements, thus improving the gear assembly's impact resistance. Simultaneously, a closed annular cavity is formed between the inner wall of the gear shaft and the outer wall of the output shaft. This annular cavity is filled with a filler material. The filler material can dissipate energy through viscosity and suppress resonance, thereby increasing the system damping of the gear assembly and absorbing waves and mechanical vibrations. Specifically, when the output shaft vibrates, part of the vibration is absorbed by the filler material, and the other part is evenly transmitted to the gear shaft, greatly reducing the vibration of the output shaft. Similarly, when the gear shaft vibrates, part of the vibration is absorbed by the filler material, and the other part is evenly transmitted to the output shaft. Therefore, by using filler material, the vibration of a single component is converted into a shared load by the gear shaft, output shaft, and filler material, thereby improving the gear assembly's resistance to impact loads, enhancing its support stiffness to increase its load-bearing capacity, transmitting greater power, improving the gear assembly's safety and reliability, and ultimately improving its service performance.

[0017] 2. In this invention, filler material is injected into the annular cavity through the feeding channel. By setting different injection pressures and injecting filler material of different densities, the stiffness and damping of the gear assembly are changed, thereby improving the applicability of the gear assembly, enabling it to adapt to different complex working conditions, and improving the service performance of the gear assembly under different complex working conditions.

[0018] 3. In this invention, the filler is a high-viscosity lubricating oil, and the high-viscosity lubricating oil contains mixed additives. The three-dimensional network of organic bentonite and the suspended core-shell particles give the filler extremely high viscoelasticity and thixotropy. When vibration or sound waves are transmitted to the filler, the energy generated by the vibration or sound waves forces relative displacement and friction between the organic bentonite layer and the core-shell particles, while destroying and rebuilding the three-dimensional network structure. This process causes most of the mechanical energy to be converted into heat energy and dissipated through internal friction, effectively absorbing vibration and mechanical waves, and thus significantly suppressing the vibration generated by the gear shaft or output shaft or the sound waves generated by gear meshing.

[0019] 4. In this invention, paraffin wax is added to the high-viscosity lubricating oil. The paraffin wax shell has an extremely high specific heat capacity near its solid-liquid phase transition point. When vibration energy is converted into heat energy, it causes the temperature of the high-viscosity lubricating oil to rise. When the temperature rises to the phase transition point, the paraffin wax undergoes a phase transition. The phase transition process absorbs a large amount of heat, thereby stabilizing the high-viscosity lubricating oil and keeping it essentially unchanged. At the same time, when the gear shaft or output shaft vibrates, the gear assembly accumulates energy at a specific frequency, causing the amplitude of the gear assembly to increase sharply and the temperature to rise. At this time, the melting phase transition of paraffin wax can absorb this energy, thereby effectively smoothing the resonance peak and preventing the amplitude from increasing infinitely.

[0020] 5. In this invention, the core-shell particles suspended in the three-dimensional network are themselves tiny dampers. Under vibration, these solid particles will undergo inelastic collisions and friction with the surrounding gel network and base oil, consuming energy. At the same time, there are large phase interfaces inside the material, such as bentonite-oil interface, paraffin shell-oil interface, and graphite / MoS2 core-paraffin interface. When vibration waves (sound waves) propagate in the material, they encounter interfaces and undergo scattering, refraction, and reflection. This process will seriously interfere with the wave propagation path and greatly attenuate the wave intensity.

[0021] 6. In this invention, a protrusion is provided on the outer wall of the output shaft inside the annular cavity. During the rotation of the output shaft, the protrusion can stir the filler material and prevent the core and shell particles from settling. Attached Figure Description

[0022] Figure 1 This is a structural schematic diagram of a variable stiffness gear assembly.

[0023] Figure 2 yes Figure 1 A magnified view of a portion of point A in the middle.

[0024] Figure 3 This is a side view of the variable stiffness gear assembly.

[0025] Figure 4 This is a schematic diagram of the debugging of the variable stiffness gear assembly.

[0026] Figure 5 This is a schematic diagram of a gear transmission device.

[0027] Reference numerals: 1. Gear shaft; 101. First connecting flange; 102. First rolling area; 2. Output shaft; 201. External spline; 202. Annular groove; 203. Variable diameter section; 204. Second rolling area; 3. Internal gear sleeve; 301. Second connecting flange; 302. Internal spline; 303. Stop block; 4. Feed channel; 401. Sealing component; 5. Annular cavity; 6. Outward expansion mounting area; 7. Sealing ring; 8. Arc-shaped pad; 801. Connecting bolt; 9. Second circular runout detector; 10. First circular runout detector; 11. Three-jaw chuck; 12. Ejector pin; 13. High-speed gear assembly; 1301. Input shaft; 1302. High-speed transmission gear; 14. Housing; 1401. Sliding bearing. Detailed Implementation

[0028] The technical solution of the present invention will be further described in detail below with reference to specific embodiments. Parts not described or disclosed in detail in the following embodiments of the present invention should be understood as prior art known or should be known by those skilled in the art.

[0029] Example 1 A variable stiffness gear assembly, such as Figure 1 As shown, the device includes a gear shaft 1 with a through hole at its axial position and an output shaft 2 coaxially disposed within the through hole. An annular cavity 5 is formed between the inner wall of the gear shaft 1 and the outer wall of the output shaft 2. The output shaft 2 is a stepped shaft, and there are variable diameter sections 203 on the output shaft 2 near both ends of the annular cavity 5. There is a small diameter section between the two variable diameter sections 203. The diameter of the small diameter section is smaller than the diameter of the variable diameter section 203, and the outer wall of the variable diameter section 203 fits against the inner wall of the gear shaft 1, so that the outer wall of the small diameter section, the end face of the variable diameter section 203 near the small diameter section, and the inner wall of the gear shaft 1 enclose and form an annular cavity 5.

[0030] One end of the annular cavity 5 is sealed by an internal gear sleeve 3 with an internal spline 302, and the internal gear sleeve 3 is fixedly connected to one end of the gear shaft 1. The shaft end of the output shaft 2 extends into the internal gear sleeve 3 and engages with the internal spline 302 of the internal gear sleeve 3 through an external spline 201 for transmission. The other end of the output shaft 2 extends out of the through hole and is connected to other equipment for transmission. A stop block 303 extending toward the center of the internal gear sleeve 3 is fixedly provided at the end of the internal gear sleeve 3 away from the gear shaft 1. The stop block 303 has an annular structure, and the end face of the output shaft 2 extending into the internal gear sleeve 3 abuts against the stop block 303. The gear shaft 1 and the internal gear sleeve 3 are connected as follows: the end of the gear shaft 1 is integrally connected to a first connecting flange 101, and the end of the internal gear sleeve 3 near the gear shaft 1 is integrally connected to a second connecting flange 301. The first connecting flange 101 and the second connecting flange 301 are connected by fixing bolts.

[0031] The other end of the annular cavity 5 is sealed by an arc-shaped gasket 8 located between the outer walls of the gear shaft 1 and the output shaft 2. The end of the gear shaft 1 facing away from the inner gear sleeve 3 has a notch. The notch is annular in shape, and its diameter gradually increases along the axial direction of the gear shaft 1, expanding outwards. This creates an expanded mounting area 6 between the inner wall of the notch and the outer wall of the output shaft 2 for mounting the arc-shaped gasket 8. The arc-shaped gasket 8 has a wedge-shaped cross-section, such as... Figure 2 and Figure 3 As shown, the outer wall of the arc-shaped pad 8 is an inclined surface and contacts the side wall of the notch, while the inner wall of the arc-shaped pad 8 contacts the outer wall of a variable diameter section 203 of the output shaft 2. There are multiple arc-shaped pads 8, such as... Figure 3 As shown, in this embodiment, there are eight arc-shaped pads 8. The arc-shaped pads 8 are wedged into the extended mounting area 6, and the ends of the arc-shaped pads 8 located outside the extended mounting area 6 are fixedly connected to the end face of the gear shaft 1 via connecting bolts 801. Adjusting the preload of the connecting bolts 801 can adjust the axial position of the output shaft 2. This extends the power transmission path of the gear assembly, allowing for a larger torsional angle under the same torsional deformation requirements, further improving the impact resistance of the gear assembly.

[0032] The annular cavity 5 is filled with a filler material. The filler material is selected from materials with good viscosity energy dissipation and resonance suppression properties, such as high viscosity lubricating oil or grease. In this embodiment, the filler material is high viscosity lubricating oil.

[0033] To prevent leakage of filler material, a sealing ring 7 is provided between the outer wall of the variable diameter section 203 and the inner wall of the gear shaft 1 for sealing. The sealing ring 7 is a labyrinth seal.

[0034] At least one feed channel 4 is provided on the gear shaft 1 for injecting filler material into the annular cavity 5. One end of the feed channel 4 is connected to the annular cavity 5, and the other end of the feed channel 4 can be closed by a sealing member 401. The feed channel 4 can extend radially along the gear shaft 1 or extend at a certain angle to the radial direction of the gear shaft 1. In this embodiment, the feed channel 4 extends radially along the gear shaft 1. The number of feed channels 4 is 1-4. In this embodiment, the number of feed channels 4 is 2 and they are evenly distributed around the circumference of the gear shaft 1. The end of the feed channel 4 near the output shaft 2 extends to the inner wall of the gear shaft 1 and is connected to the annular cavity 5. The other end of the feed channel 4 extends to the outer wall of the gear shaft 1. The inner wall of the end of the output shaft 2 facing away from the output shaft 2 is provided with an internal thread, and the outer wall of the sealing member 401 is provided with an external thread that mates with the internal thread. Before the variable stiffness gear assembly operates, the rotating sealing member 401 connects the feeding assembly to the end of the feed channel 4 opposite to the output shaft 2, filling the annular cavity 5 with the required filler material. After filling, the rotating sealing member 401 seals the feed channel 4. By setting different injection pressures and injecting filler materials of different densities, the stiffness and damping of the gear assembly are changed, thereby improving the applicability of the gear assembly, enabling it to adapt to different complex working conditions, and improving the service performance of the gear assembly under different complex working conditions.

[0035] The filler material can dissipate energy through viscosity and suppress resonance, thereby increasing the system damping of the gear assembly and absorbing waves and mechanical vibrations. Specifically, when the output shaft 2 vibrates, part of the vibration is absorbed by the filler material, and the other part is evenly transmitted to the gear shaft 1, greatly reducing the vibration of the output shaft 2. Similarly, when the gear shaft 1 vibrates, part of the vibration is absorbed by the filler material, and the other part is evenly transmitted to the output shaft 2. Therefore, the vibration of a single component is transformed into a shared burden by the gear shaft 1, the output shaft 2, and the filler material through the filler material. When the gear shaft 1 is subjected to radial force or bending moment, the filler material transmits part of the force to the output shaft 2, so that the gear shaft 1 and the output shaft 2 share the radial force or bending moment on the gear shaft 1. Similarly, when the output shaft 2 is subjected to radial force or bending moment, the filler material transmits part of the force to the gear shaft 1, so that the gear shaft 1 and the output shaft 2 share the radial force or bending moment on the output shaft 2. This improves the gear assembly's resistance to impact loads, enhances its support stiffness to increase its load-bearing capacity, transmits greater power, and improves its safety and reliability, thereby enhancing its service performance.

[0036] The annular channel, located at the external teeth of gear shaft 1, could potentially affect the transmission of gear shaft 1. Therefore, an annular groove 202 is coaxially formed on gear shaft 1, with the annular groove 202 located at the axial center of gear shaft 1, creating a filler injection section on gear shaft 1. The diameter of the filler injection section is smaller than the outer diameter of gear shaft 1. Feed channel 4 is located within the filler injection section, and the end of feed channel 4 facing away from the annular cavity 5 extends to the bottom of the annular groove 202. That is, the end of feed channel 4 is lower than the external teeth of gear shaft 1, thus preventing it from affecting the normal transmission of gear shaft 1.

[0037] Example 2 This embodiment is an improvement on Embodiment 1. Its main structure is the same as Embodiment 1, but the improvement lies in the following: In this embodiment, the filler is a high-viscosity lubricating oil, which contains 40% by mass of a mixed additive. According to the mass ratio, the mixed additive consists of 4 parts organic bentonite, 12 parts paraffin wax, 5 parts modified graphite, 6 parts modified molybdenum disulfide, and 1.6 parts polar activator. The polar activator is a mixture of methanol and water in a 1:1 volume ratio. The organic bentonite is a commercially available, mature product; the modified molybdenum disulfide has a purity of not less than 99% and a particle size of 1-5 μm; the modified graphite is flake graphite with a particle size of 5-1 μm; the paraffin wax is refined grade paraffin wax with a melting point of 58-62℃; and the base oil is selected from API Group III base oils (such as 10W-40 engine oil) or anhydrous grease (such as lithium-based grease).

[0038] The method for preparing the filler in this embodiment includes the following steps: 1) Preparation of modified graphite and modified molybdenum disulfide Graphite and molybdenum disulfide were dispersed separately in anhydrous ethanol and ultrasonically dispersed for 30 min to ensure full dispersion. Then, 3% by mass of silane coupling agent KH-550 was added to each of them. The reaction was carried out under magnetic stirring at 70℃ for 2 h. After the reaction was completed, the mixture was centrifuged and washed with ethanol, and then thoroughly dried in a vacuum drying oven at 75℃ to obtain modified graphite and modified molybdenum disulfide.

[0039] 2) Preparation of core-shell melt The paraffin wax was heated until completely melted, and then the modified graphite and modified molybdenum disulfide prepared in step 1) were slowly added to the molten paraffin wax. At the same time, a high-speed shear disperser was used to mix the mixture at a speed of 10,000 rpm for 10 minutes to form a uniform core-shell melt.

[0040] 3) Preparation of the oil phase In a reactor equipped with heating and stirring functions, base oil and organobentonite are added. Under slow stirring, a polar activator is added, the temperature is raised to 60°C, and stirring is continued for 30 minutes to allow the organobentonite to initially swell and form a uniform oil slurry. 4) Thermal emulsification The oil slurry prepared in step 3) is transferred into a high-speed shear disperser. Then, under high-speed shear conditions of 8000 rpm, the core-shell melt prepared in step 2) is slowly added dropwise to the oil slurry. The oil is then continuously sheared and emulsified at 65°C for 30 minutes to form a coarse emulsion of "oil-encapsulated solid core-shell particles". The crude emulsion prepared in step 4) is cooled to room temperature under slow stirring to form a paste; The cooled paste is mechanically homogenized using a three-roll mill or a high-pressure homogenizer, and the homogenization process is repeated twice to obtain a high-viscosity lubricating oil.

[0041] The aforementioned high-viscosity lubricating oil needs to be heated to improve its fluidity before being injected into the cavity.

[0042] Example 3 This embodiment is an improvement on Embodiment 1. Its main structure is the same as Embodiment 1, but the improvement lies in the following: In this embodiment, the filler is a high-viscosity lubricating oil, which is a paste formed by adding mixed additives to the base oil. Specifically, the high-viscosity lubricating oil contains 10% of its mass of mixed additives. According to the mass ratio, the mixed additives consist of 8 parts organobentonite, 6 parts paraffin wax, 3 parts modified graphite, 3 parts modified molybdenum disulfide, and 4 parts a polar activator. The polar activator is a mixture of methanol and water in a 1:1 volume ratio.

[0043] The method for preparing the filler in this embodiment includes the following steps: 1) Preparation of modified graphite and modified molybdenum disulfide Graphite and molybdenum disulfide were dispersed separately in anhydrous ethanol and ultrasonically dispersed for 30 min to ensure full dispersion. Then, 5% by mass of silane coupling agent KH-550 was added to each, and the mixture was magnetically stirred at 80℃ for 4 h. After the reaction was completed, the mixture was centrifuged and washed with ethanol, and then thoroughly dried in a vacuum drying oven at 85℃ to obtain modified graphite and modified molybdenum disulfide.

[0044] 2) Preparation of core-shell melt The paraffin wax was heated until completely melted, and then the modified graphite and modified molybdenum disulfide prepared in step 1) were slowly added to the molten paraffin wax. At the same time, a high-speed shear disperser was used to mix the mixture at a speed of 12,000 rpm for 15 minutes to form a uniform core-shell melt.

[0045] 3) Preparation of the oil phase In a reactor equipped with heating and stirring functions, base oil and organobentonite are added. Under slow stirring, a polar activator is added, the temperature is raised to 65°C, and stirring is continued for 60 minutes to allow the organobentonite to initially swell and form a uniform oil slurry. 4) Thermal emulsification The oil slurry prepared in step 3) is transferred into a high-speed shear disperser. Then, under high-speed shear conditions of 12,000 rpm, the core-shell melt prepared in step 2) is slowly added dropwise to the oil slurry. At 70°C, it is continuously emulsified by high-speed shear for 45 minutes to form a crude emulsion of "oil-encapsulated solid core-shell particles". The crude emulsion prepared in step 4) is cooled to room temperature under slow stirring to form a paste; The cooled paste is mechanically homogenized using a three-roll mill or a high-pressure homogenizer, and the homogenization process is repeated 2-4 times to obtain a high-viscosity lubricating oil.

[0046] The aforementioned high-viscosity lubricating oil needs to be heated to improve its fluidity before being injected into the cavity.

[0047] Example 4 This embodiment is an improvement on embodiment 1. Its main structure is the same as that of embodiment 1. The improvement is that the filler is high-viscosity lubricating oil, which contains 25% of its mass of mixed additives. According to the mass ratio, the mixed additives consist of 6 parts of organic bentonite, 14 parts of paraffin wax, 4 parts of modified graphite, 4 parts of modified molybdenum disulfide, and 2 parts of polar activator. The polar activator is a mixture of methanol and water in a 1:1 volume ratio.

[0048] The method for preparing the filler in this embodiment includes the following steps: 1) Preparation of modified graphite and modified molybdenum disulfide Graphite and molybdenum disulfide were dispersed separately in anhydrous ethanol and ultrasonically dispersed for 30 min to ensure full dispersion. Then, 4% by mass of silane coupling agent KH-550 was added to each, and the reaction was carried out under magnetic stirring at 75℃ for 3 h. After the reaction was completed, the mixture was centrifuged and washed with ethanol, and then thoroughly dried in a vacuum drying oven at 80℃ to obtain modified graphite and modified molybdenum disulfide.

[0049] 2) Preparation of core-shell melt The paraffin wax was heated until completely melted, and then the modified graphite and modified molybdenum disulfide prepared in step 1) were slowly added to the molten paraffin wax. At the same time, a high-speed shear disperser was used to mix the mixture at a speed of 11,000 rpm for 13 minutes to form a uniform core-shell melt.

[0050] 3) Preparation of the oil phase In a reactor equipped with heating and stirring functions, base oil and organobentonite are added. Under slow stirring, a polar activator is added, the temperature is raised to 63°C, and stirring is continued for 45 minutes to allow the organobentonite to initially swell and form a uniform oil slurry. 4) Thermal emulsification The oil slurry prepared in step 3) is transferred into a high-speed shear disperser. Then, under high-speed shear conditions of 10,000 rpm, the core-shell melt prepared in step 2) is slowly added dropwise to the oil slurry. At 68°C, it is continuously emulsified by high-speed shear for 40 minutes to form a crude emulsion of "oil-encapsulated solid core-shell particles". The crude emulsion prepared in step 4) is cooled to room temperature under slow stirring to form a paste; The cooled paste is mechanically homogenized using a three-roll mill or a high-pressure homogenizer, and the homogenization process is repeated three times to obtain a high-viscosity lubricating oil.

[0051] The aforementioned high-viscosity lubricating oil needs to be heated to improve its fluidity before being injected into the cavity.

[0052] Example 5 This embodiment is an improvement on Embodiment 2, Embodiment 3, or Embodiment 4. Its main structure is the same as Embodiment 1, but the improvement lies in the following: several protrusions are distributed axially on the outer wall of the output shaft 2 within the annular cavity 5, and the height of the protrusions does not exceed 40% of the width of the annular cavity 5, preferably 10-20%. In this embodiment, the protrusions are multiple and spirally distributed, so that during the rotation of the output shaft, the spirally distributed protrusions can agitate the filler material, preventing the core-shell particles in the filler material from settling.

[0053] Example 6 A method for adjusting a variable stiffness gear assembly, wherein the variable stiffness gear assembly is driven to rotate at its operating speed, such as... Figure 4 As shown, the inner gear sleeve 3 is held by a three-jaw chuck 11, and the output shaft 2 is pressed against the end away from the inner gear sleeve 3 by a push pin 12. The variable stiffness gear assembly is driven to rotate by the drive source on the machine tool.

[0054] A first circular runout detector 10 and a second circular runout detector 9 are used to simultaneously detect the mechanical runout of the gear shaft 1 and the output shaft 2. The first circular runout detector 10 detects the mechanical runout of the first rolling area 102 on the gear shaft 1; the second circular runout detector 9 detects the mechanical runout of the second rolling area 204 on the output shaft 2. The rolling accuracy of the first rolling area 102 and the second rolling area 204 is determined first by the data detected by the first circular runout detector 10 and the second circular runout detector 9. Then, based on the data detected by the first circular runout detector 10, the axial center position of the output shaft 21 is adjusted. According to the runout data of the two circular runout detectors, the preload of each connecting bolt 801 is adjusted individually to achieve individual adjustment of each arc-shaped pad 8 until the difference between the data detected by the second circular runout detector 9 and the data detected by the first circular runout detector 10 is less than a preset value. This indicates that the axial center positions of the output shaft 2 and the gear shaft 1 have been adjusted to be consistent, achieving concentricity, and their coaxiality meets the specified accuracy level.

[0055] Example 7 A high-speed, heavy-duty gear transmission device includes a housing 14, within which a high-speed gear assembly 13 and a low-speed gear assembly are disposed. The high-speed gear assembly 13 includes an input shaft 1301 and a high-speed transmission gear 1302 fixedly sleeved on the input shaft 1301, with the input shaft 1301 rotatably connected to the housing 14 via a sliding bearing 1401. The low-speed gear assembly is a calibrated variable stiffness gear assembly, with an output shaft 2 rotatably connected to the housing 14 via a sliding bearing 1401, and a gear shaft 1 rotatably connected to the housing 14 via a sliding bearing 1401, with both ends of the gear shaft 1 extending out of the housing 14.

[0056] The above description of the disclosed embodiments enables those skilled in the art to make or use the invention. Various modifications to these embodiments will be readily apparent to those skilled in the art, and the general principles defined herein may be implemented in other embodiments without departing from the spirit or scope of the invention. Therefore, the invention is not to be limited to the embodiments shown herein, but is to be accorded the widest scope consistent with the principles and novel features disclosed herein.

Claims

1. A variable stiffness gear assembly, characterized by: The gear shaft (1) with a through hole at the position of the shaft center and the output shaft (2) coaxially arranged in the through hole, and the annular cavity (5) is formed between the inner side wall of the gear shaft (1) and the outer side wall of the output shaft (2), one end of the annular cavity (5) is sealed by the inner gear sleeve (3) with internal spline (302) inside, and the inner gear sleeve (3) is fixedly connected with one end of the gear shaft (1), the other end of the annular cavity (5) is sealed by the arc-shaped pad (8) between the inner side wall of the gear shaft (1) and the outer side wall of the output shaft (2); the shaft end of the output shaft (2) extends into the inner gear sleeve (3) and is in meshing transmission with the internal spline (302) of the inner gear sleeve (3) through the external spline (201); the gear shaft (1) is provided with a feeding channel (4) for injecting filling material into the annular cavity (5), and the end of the feeding channel (4) is sealed by the plugging piece (401).

2. A variable stiffness gear assembly as claimed in claim 1, wherein: The end of the inner gear sleeve (3) away from the gear shaft (1) is fixedly provided with a stop block (303) extending towards the center of the inner gear sleeve (3), and the end face of the output shaft (2) extending into the inner gear sleeve (3) abuts against the stop block (303).

3. A variable stiffness gear assembly as in claim 1, wherein: The output shaft (2) is a stepped shaft, and the variable diameter portion (203) is arranged on the output shaft (2) near the positions of the two ends of the annular cavity (5), and the sealing ring (7) is arranged between the outer side wall of the variable diameter portion (203) and the inner side wall of the gear shaft (1) for sealing.

4. A variable stiffness gear assembly as in claim 1, wherein: The end of the gear shaft (1) away from the inner gear sleeve (3) has a notch, and the outer expansion mounting area (6) for mounting the arc-shaped pad (8) is formed between the inner side wall of the notch and the outer side wall of the output shaft (2).

5. A variable stiffness gear assembly as in claim 1, wherein: A plurality of protrusions are distributed on the outer wall of the output shaft (2) in the axial direction.

6. A variable stiffness gear assembly as in claim 1, wherein: The filling material is high-viscosity lubricating oil.

7. A variable stiffness gear assembly according to claim 6, wherein: The high-viscosity lubricating oil contains 10-40% of mixed additives by mass, and the mixed additives are composed of 4-8 parts of organic bentonite, 12-16 parts of paraffin, 3-5 parts of modified graphite, 3-6 parts of modified molybdenum disulfide, and 1.6-4 parts of polar activator by mass ratio, and the polar activator is a mixture of methanol and water in a volume ratio of 1:

1.

8. A method of setting up a variable stiffness gear assembly as claimed in any one of claims 1 to 7, characterised by: The variable stiffness gear assembly is driven to rotate at its working speed, and the first roundness detector (10) and the second roundness detector (9) are used to detect the mechanical runout of the gear shaft (1) and the output shaft (2) at the same time, and the data detected by the first roundness detector (10) is used as a reference to adjust the pad (8) to adjust the shaft center position of the output shaft (2), until the difference between the data detected by the second roundness detector (9) and the data detected by the first roundness detector (10) is less than a preset value.

9. A high speed heavy duty gear transmission comprising a housing (14) having a high speed gear assembly (13) and a low speed gear assembly (12) disposed within the housing (14) and in meshing engagement, characterised in that: The low-speed gear assembly is the variable stiffness gear assembly according to any one of claims 1-7.

10. A high speed heavy duty gear arrangement as claimed in claim 9, characterised in that: The high-speed gear assembly (13) comprises an input shaft (1301) and a high-speed transmission gear (1302) fixedly sleeved on the input shaft (1301), and the input shaft (1301) is rotationally connected with the box body (14) through a sliding bearing (1401); the gear shaft (1) is rotationally connected with the box body (14) through the sliding bearing (1401), and both ends of the gear shaft (1) extend out of the box body (14).

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