Gearbox balancing device

Abstract

The present application belongs to the technical field of correction device, disclose a kind of gear box balancing correction device, rotating shaft is rigidly connected with sleeve in gear box, base is matched with sleeve air gap and installs excitation coil stator, double cup mouth opposite flexible gear is engaged by rigid gear ring in sleeve, eccentric block is arranged in flexible gear cup bottom, internal wave generator, wave generator is connected with rotating shaft by bearing and integrated energy transmission cylinder, and magnetic hysteresis rotor is arranged in the end of energy transmission cylinder;When working, double excitation coil stator independently generates rotating magnetic field, and independently angular deflection of wave generator is driven through air gap coupling, and the included angle of eccentric block is adjusted and controlled to synthesize reverse compensation centrifugal force to offset unbalanced vibration;Device structure is compact, control is accurate, transmission is stable, non-contact transmission improves high-speed reliability, solves the problem of redundant structure and insufficient precision of traditional device.

Description

Technical Field

[0001] This invention belongs to the technical field of calibration devices, and specifically relates to a gearbox balance calibration device. Background Technology

[0002] The gearbox is a core component of the power transmission system. When its internal rotating shaft operates at high speed, it is prone to unbalanced vibration due to factors such as manufacturing tolerances, assembly errors, and wear under operating conditions. This vibration can reduce transmission efficiency, accelerate the wear of bearings and gears, and even cause equipment failure. Therefore, real-time balancing and correction of the rotating shaft is crucial.

[0003] The current method for balancing and correcting the rotating shaft of a gearbox has significant drawbacks: 1. Offline balancing requires disassembling the gearbox and then using a dynamic balancing machine for counterweighting, which is cumbersome, has long downtime, and cannot be adapted to dynamic working conditions. 2. Existing online active balancing devices mostly adopt a split transmission component layout, with large axial / radial dimensions, making it difficult to adapt to the limited space inside the gearbox. There are gaps and cumulative errors in the transmission links, the angle control accuracy of the eccentric components is low, and it cannot offset small imbalances. The power transmission path is complex, and the adjustment of unbalanced vibrations is lagging, making it difficult to achieve real-time compensation. Summary of the Invention

[0004] In view of the problems mentioned above in the background art, the object of the present invention is to provide a gearbox balancing correction device.

[0005] To achieve the above-mentioned technical objectives, the technical solution adopted by the present invention is as follows: A gearbox balancing and correction device includes a gearbox with a rotating shaft installed, the rotating shaft rotating inside the gearbox and transmitting power, a base fixedly installed on the gearbox, a sleeve rotatably connected to the base, the base and the sleeve having a non-contact air gap fit, and an excitation coil stator installed at the air gap fit position between the base and the sleeve. The sleeve is rigidly connected to the rotating shaft via a flat key. A rigid gear ring is integrally formed and installed at the center of the sleeve's interior. Two flexible gears mesh with the rigid gear ring, each with two fewer teeth than the rigid gear ring. The two flexible gears are distributed axially along the rotating shaft with their cups facing each other. An eccentric block is fixedly installed on the outer side of the cup bottom of each flexible gear. A wave generator is fitted inside each flexible gear. A bearing is installed between the wave generator and the rotating shaft. An energy-transmitting cylinder is integrally connected to the inner ring of the wave generator. A hysteresis rotor is fixedly installed on the energy-transmitting cylinder after it extends to the outer side of the cup bottom of the flexible gear. The two sets of excitation coil stators independently generate controllable rotating magnetic fields, which are coupled to the corresponding hysteresis rotors through the air gap between the base and the sleeve. This drives the two wave generators to deflect independently relative to the rotating shaft, thereby precisely controlling the relative angle between the two eccentric blocks to synthesize a compensating centrifugal force that is equal in magnitude and opposite in direction to the unbalance of the rotating shaft.

[0006] Furthermore, a gap is left between the outer wall of the energy transfer cylinder and the inner cavity wall of the flexible wheel. The energy transfer cylinder extends through the gap to the outer side of the cup bottom of the flexible wheel to avoid interference between the energy transfer cylinder and the flexible wheel, ensure the freedom of elastic deformation of the flexible wheel, and optimize the spatial layout of the components and compress the radial dimension of the device.

[0007] Furthermore, the eccentric block is a fan-shaped structure, and the centers of mass of the two eccentric blocks are located at radially symmetrical positions on the rotation axis. The fan-shaped structure facilitates precise control of the center of mass position, and the radially symmetrical layout enables rapid vector synthesis of unbalanced compensation forces, thereby improving the response efficiency of balance correction.

[0008] Further specifying, the bearing is a deep groove ball bearing, with the inner ring of the deep groove ball bearing having an interference fit with the rotating shaft and the outer ring having an interference fit with the inner hole of the wave generator. The deep groove ball bearing is adapted to the small angular deflection movement of the wave generator, and the interference fit eliminates transmission clearance, ensuring the control accuracy of the angular deflection of the wave generator.

[0009] Furthermore, dustproof sealing rings are installed on the inner sides of both ends of the sleeve. The lip of the dustproof sealing ring is in interference contact with the outer wall of the rotating shaft to prevent oil and dust from entering the sleeve, protect the internal precision transmission components, and extend the service life of the device.

[0010] Furthermore, the hysteresis rotor has an annular structure, with a radial gap between the outer wall of the hysteresis rotor and the inner wall of the sleeve. The annular structure makes the magnetic field coupling more uniform, and the radial gap avoids contact and friction between the hysteresis rotor and the inner wall of the sleeve when rotating, thus reducing energy loss.

[0011] Furthermore, the tooth profile of the rigid wheel gear ring is an involute tooth profile, and the tooth profile of the flexible wheel is adapted to the tooth profile of the rigid wheel gear ring. The involute tooth profile meshing transmission is smooth, with low impact and low noise, thereby improving the transmission accuracy and reliability of the flexible wheel and the rigid wheel.

[0012] Furthermore, the energy-transmitting cylinder and the wave generator are formed by an integrated forging process, which reduces the assembly gap between the separate parts, improves the structural rigidity, avoids lag in the power transmission process, and ensures the accurate transmission of angular deflection.

[0013] Furthermore, the excitation current of the two sets of excitation coil stators is output by an independent controller to adjust the angular deflection angle of the two wave generators respectively, thereby achieving continuous stepless control of the relative angle between the two eccentric blocks. The independent control of the two stators realizes the decoupling adjustment of the two wave generators, and the continuous stepless control can cover the full range of unbalance compensation, improving the correction accuracy.

[0014] Furthermore, the inner wall of the sleeve and the root of the tooth of the rigid wheel gear ring are provided with annular oil reservoirs, which are filled with gear grease to continuously provide lubrication for the meshing parts of the rigid wheel and the flexible wheel, reduce tooth surface wear, and extend the service life of the meshing pair.

[0015] The beneficial effects of using the present invention are as follows: This device adopts an axially distributed form with the cups of the two flexible wheels facing each other. Combined with the gap design between the energy transmission cylinder and the inner cavity of the flexible wheel, the radial and axial dimensions of the device are effectively compressed, making it suitable for the limited installation space inside the gearbox. At the same time, the sleeve and the rigid wheel gear ring are integrally molded, reducing the assembly steps of the separate parts and improving the overall structural rigidity. Two sets of excitation coil stators output excitation current through independent controllers, realizing decoupled independent angular deflection control of the dual-wave generator. Combined with the radially symmetrical layout of the fan-shaped eccentric blocks, the relative angle between the eccentric blocks can be precisely adjusted to synthesize a compensating centrifugal force that perfectly matches the unbalance of the rotating shaft. The interference fit of the deep groove ball bearing and the integrated forging process of the energy transfer cylinder and the wave generator eliminate transmission clearance, further ensuring the control accuracy and response efficiency of the angular deflection. The rigid gear ring and the flexible gear adopt a matching involute tooth profile, resulting in less impact and lower noise during meshing, thus improving transmission stability. The dustproof sealing rings at both ends of the sleeve can prevent oil and dust from entering, and the annular oil reservoir at the tooth root continuously provides lubrication for the meshing pair, reducing component wear and extending the overall service life of the device. The base and sleeve are connected by an air gap non-contact fitting, and power is transmitted through magnetic field coupling, which avoids the friction loss and mechanical wear of traditional contact transmission. At the same time, the structural design of the annular hysteresis rotor makes the magnetic field coupling more uniform, further improving the operational reliability of the device under high-speed conditions. Attached Figure Description

[0016] The present invention can be further illustrated by the non-limiting embodiments given in the accompanying drawings; Figure 1 This is a schematic diagram of an embodiment of a gearbox balancing correction device according to the present invention; Figure 2 for Figure 1 A schematic diagram of the cross-sectional structure; Figure 3 This is a schematic diagram of the sleeve position according to an embodiment of the gearbox balancing correction device of the present invention; Figure 4 This is a schematic diagram of the flexible wheel position in an embodiment of the gearbox balancing correction device of the present invention; Figure 5 This is a cross-sectional structural diagram of the position of the rotating shaft in an embodiment of a gearbox balancing correction device of the present invention; Figure 6 for Figure 5 Enlarged structural diagram at point A in the middle; The symbols for the main components are explained below: 1. Rotating shaft; 2. Gearbox; 3. Base; 4. Sleeve; 5. Excitation coil stator; 6. Rigid wheel gear ring; 7. Flexible wheel; 8. Eccentric block; 9. Wave generator; 10. Bearing; 11. Energy transfer cylinder; 12. Hysteresis rotor. Detailed Implementation

[0017] To enable those skilled in the art to better understand the present invention, the technical solution of the present invention will be further described below in conjunction with the accompanying drawings and embodiments.

[0018] like Figures 1-6 As shown, a gearbox balancing correction device of the present invention includes a gearbox 2 on which a rotating shaft 1 is installed. The rotating shaft 1 rotates in the gearbox 2 and transmits power. A base 3 is fixedly installed in the gearbox 2. A sleeve 4 is rotatably connected to the base 3. The base 3 and the sleeve 4 are in a non-contact air gap fit. An excitation coil stator 5 is installed at the air gap fit position between the base 3 and the sleeve 4. Sleeve 4 is rigidly connected to rotating shaft 1 via a flat key. A rigid gear ring 6 is integrally formed and installed at the center of sleeve 4. Two flexible wheels 7 mesh with the rigid gear ring 6. The number of teeth on the two flexible wheels 7 is two fewer than that on the rigid gear ring 6. The two flexible wheels 7 are distributed axially along rotating shaft 1 with their cups facing each other. An eccentric block 8 is fixedly installed on the outer side of the cup bottom of each flexible wheel 7. A wave generator 9 is adapted to be installed inside each flexible wheel 7. A bearing 10 is installed between the wave generator 9 and rotating shaft 1. An energy transmission cylinder 11 is integrally connected to the inner ring of the wave generator 9. After the energy transmission cylinder 11 extends to the outer side of the cup bottom of the flexible wheel 7, a hysteresis rotor 12 is fixedly installed. Two sets of excitation coil stators 5 independently generate controllable rotating magnetic fields, which are coupled to the corresponding hysteresis rotors 12 through the air gap between the base 3 and the sleeve 4, driving the two wave generators 9 to deflect independently relative to the rotating shaft 1, thereby precisely controlling the relative angle between the two eccentric blocks 8 to synthesize a compensating centrifugal force that is equal in magnitude and opposite in direction to the unbalance of the rotating shaft 1.

[0019] In this embodiment, a rotating shaft 1 is installed inside the gearbox 2. The rotating shaft 1 rotates at high speed inside the gearbox 2 to complete the power transmission task. A base 3 is fixedly installed on the inner wall of the gearbox 2. The base 3 and the sleeve 4 are arranged coaxially and are connected by an air gap non-contact fit. Two sets of excitation coil stators 5 are installed on the base 3 at the positions corresponding to the air gap fit with the sleeve 4. The sleeve 4 is rigidly connected to the rotating shaft 1 by a flat key to ensure that the two rotate synchronously. A rigid gear ring 6 is integrally formed at the center of the inner wall of the sleeve 4. Two flexible gears 7 are meshed and matched on the outer side of the rigid gear ring 6. The number of teeth of the two flexible gears 7 is two fewer than the number of teeth of the rigid gear ring 6. Two flexible wheels 7 are arranged sequentially along the axial direction of the rotating shaft 1 with their cup mouths facing each other. An eccentric block 8 is fixedly installed on the outer side of the cup bottom of each flexible wheel 7. A wave generator 9 is adapted to be installed in the internal cavity of each of the two flexible wheels 7. A bearing 10 is installed between the inner hole of the wave generator 9 and the rotating shaft 1. An energy transmission cylinder 11 is integrally connected to the inner ring of the wave generator 9. The energy transmission cylinder 11 extends toward the cup bottom of the flexible wheel 7 until it passes through the cup bottom of the flexible wheel 7 and extends to the outer side of the cup bottom of the flexible wheel 7. A hysteresis rotor 12 is fixedly installed at the end of the energy transmission cylinder 11 away from the wave generator 9. The hysteresis rotor 12 corresponds one-to-one with the excitation coil stator 5 and maintains an air gap fit. When the rotating shaft 1 rotates at high speed and generates unbalanced vibration, the control system detects the vibration signal and analyzes the magnitude and phase of the unbalance. It then outputs independent controllable currents to the two sets of excitation coil stators 5. After being energized, the two sets of excitation coil stators 5 generate rotating magnetic fields with adjustable intensity and phase. These magnetic fields pass through the air gap between the base 3 and the sleeve 4, precisely acting on the corresponding annular hysteresis rotor 12 inside the sleeve 4. The hysteresis rotor 12 generates torque under the influence of the magnetic field. This torque is transmitted to the wave generator 9 through the integrally formed energy transfer cylinder 11. Since the wave generator 9 is rotatably connected to the rotating shaft 1 via the bearing 10, under torque drive, the wave generator 9 can undergo a small independent angular deflection relative to the rotating shaft 1. The wave generator 9 is existing technology and can be purchased directly. The wave generator 9 is an elliptical cam with a flexible bearing. Its angular deflection directly changes the orientation of its own elliptical major axis, thereby forcing the flexible wheel 7 on its outer side to undergo elastic deformation synchronously, causing the meshing position of the flexible wheel 7 and the rigid wheel gear ring 6 to shift circumferentially. The deformation of the flexible wheel 7 drives the eccentric block 8 fixed on the outer side of its cup bottom to rotate synchronously. By independently controlling the angular deflection angle of the two wave generators 9, the relative angle between the two eccentric blocks 8 can be precisely adjusted. According to the principle of vector synthesis, the centrifugal force generated when the two eccentric blocks 8 rotate can synthesize a compensating centrifugal force that is equal in magnitude and completely opposite in direction to the unbalance of the rotating shaft 1. This compensating centrifugal force cancels the unbalanced vibration of the rotating shaft 1 in real time, realizing the online dynamic balance correction of the rotating shaft 1 of the gearbox 2. Further explanation: According to the principle of vector composition, each of the two eccentric blocks 8 generates a constant centrifugal force during rotation. The resultant vector of these two centrifugal forces is the final compensating centrifugal force. When the angle between the two eccentric blocks 8 changes, the magnitude and direction of the resultant vector are precisely controlled, thereby achieving targeted cancellation of the unbalanced vibration of the rotating shaft 1. For example, if the unbalance of the rotating shaft 1 is detected as "magnitude F1, direction radially to the left of the rotating shaft," and the initial angle between the two eccentric blocks 8 is 60°, the magnitude of the synthesized compensating centrifugal force is Fresultant1, and the direction is radially to the right and upward by 30°, which cannot completely cancel the unbalance. When the control system drives... When the two wave generators 9 deflect synchronously, increasing the angle between the two eccentric blocks 8 to 120°, according to the parallelogram law, the direction of the line connecting the ends of the centrifugal force vectors of the two eccentric blocks changes. The magnitude of the synthesized compensating centrifugal force is precisely increased to F1, and its direction is exactly along the radial right side, which is equal in magnitude and completely opposite in direction to the unbalance of the rotating shaft 1. At this time, the compensating centrifugal force can completely cancel the unbalanced vibration on the left side of the rotating shaft, thus achieving balance correction. For example, if the direction of the unbalance of the rotating shaft is deviated, it is only necessary to continue to fine-tune the angle between the two eccentric blocks to change the direction of the compensating centrifugal force, always ensuring that it is opposite to the direction of the unbalance, thus ensuring the accuracy of balance correction. The axial distribution of the two flexible wheels 7 with their cups facing each other significantly reduces the overall axial dimension of the device, adapting to the limited installation space inside the gearbox 2. The integrated design of the sleeve 4 and the rigid wheel gear ring 6 reduces the assembly steps of separate components and improves the overall structural rigidity of the device. The two sets of excitation coil stators 5 independently control the angular deflection of the dual-wave generator 9, achieving precise adjustment of the relative angle of the eccentric blocks 8. Compared with the traditional single stator and single eccentric block balancing device, it can cover a wider range of unbalance compensation, and the compensation accuracy is significantly improved. The base 3 and the sleeve 4 adopt a magnetic field coupling transmission method with air gap non-contact cooperation, avoiding the friction loss and mechanical wear of traditional contact transmission, and improving the operational reliability of the device under high-speed conditions. This non-contact transmission structure, combined with the coordinated adjustment design of the two flexible wheels and two eccentric blocks, is an innovative improvement on the existing gearbox balancing correction device, effectively solving the technical pain points of structural redundancy and insufficient control accuracy of traditional devices.

[0020] Preferably, there is a gap between the outer wall of the energy transfer cylinder 11 and the inner cavity wall of the flexible wheel 7, and the energy transfer cylinder 11 extends through the gap to the outer side of the cup bottom of the flexible wheel 7.

[0021] In this embodiment, a uniform gap is reserved between the outer wall of the energy transfer cylinder 11 and the inner cavity wall of the flexible wheel 7. The energy transfer cylinder 11 passes through the gap along the axial direction of the rotation shaft 1 and extends smoothly to the outer side of the cup bottom of the flexible wheel 7. The outer wall of the energy transfer cylinder 11 does not contact the inner cavity wall of the flexible wheel 7 throughout the entire process. Considering the differences in elastic deformation of flexure 7 of different specifications during operation, the gap width is flexibly adjusted according to the maximum deformation parameter of flexure 7. At the same time, the outer diameter of the energy transmission cylinder 11 can be adapted to the space size of the inner cavity of flexure 7 to ensure that interference between the energy transmission cylinder 11 and flexure 7 can be avoided in the assembly scenarios of different models of gearbox 2, and there is no need to further enlarge the radial dimension of the sleeve 4. Ensuring the complete freedom of elastic deformation of the flexible wheel 7 avoids transmission jamming caused by component interference. At the same time, the internal spatial layout of the sleeve 4 is optimized, further compressing the radial dimension of the device and improving the device's adaptability to gearboxes 2 of different specifications.

[0022] Preferably, the eccentric block 8 has a fan-shaped structure, and the centers of mass of the two eccentric blocks 8 are located in a radially symmetrical position on the rotation axis 1.

[0023] In this implementation case, the eccentric block 8 adopts a fan-shaped structure design. The centroids of the two eccentric blocks 8 are equidistant from the central axis of the rotating shaft 1, and the two centroids are located in radially symmetrical positions of the rotating shaft 1. After assembly, the fan-shaped arc surfaces of the two eccentric blocks 8 face the same direction. Based on the maximum imbalance requirement of the rotating shaft 1, the centrifugal force of a single eccentric block 8 can be precisely controlled by adjusting the central angle, radius or thickness of the fan-shaped eccentric block 8. At the same time, the radially symmetrical layout can be extended to a combination design of multiple eccentric blocks. When the compensation range of a single eccentric block is insufficient, the compensation capability can be further improved by increasing the number of eccentric blocks, and the newly added eccentric blocks still maintain the radial symmetry relationship with the original eccentric blocks. The fan-shaped structure facilitates precise control of the center of mass position of the eccentric block 8, improving the calculation accuracy of the centrifugal force compensation. The radially symmetrical layout makes the coordinated adjustment of the two eccentric blocks 8 more efficient, significantly shortening the response time of the compensation force. The extended multi-set eccentric block combination design can cover a wider range of imbalance compensation needs, improving the applicable operating conditions of the device.

[0024] The preferred bearing 10 is a deep groove ball bearing, with the inner ring of the deep groove ball bearing having an interference fit with the rotating shaft 1 and the outer ring having an interference fit with the inner hole of the wave generator 9.

[0025] In this embodiment, the bearing 10 is a deep groove ball bearing. The inner ring of the deep groove ball bearing is interference-fitted with the outer wall of the rotating shaft 1. The outer ring of the bearing 10 is also interference-fitted with the inner hole of the wave generator 9. During assembly, the bearing 10 is precisely pressed into the preset position by a cold pressing process. For different speed operating conditions, deep groove ball bearings 10 with different precision grades can be selected. High-precision silent deep groove ball bearings are selected for high-speed operating conditions to reduce operating noise and vibration. At the same time, the tolerance grade of the interference fit can be adjusted according to the material characteristics of the rotating shaft 1 and the wave generator 9. For easily deformable materials, a combination structure of transition fit and interference fit can be adopted to ensure backlash-free transmission while avoiding excessive assembly stress that could damage the components. The selection of deep groove ball bearing 10 is adapted to the small angular deflection motion of wave generator 9, which reduces the running resistance of the device. The interference fit design eliminates transmission clearance and ensures the control accuracy of the angular deflection of wave generator 9. The expanded accuracy level and tolerance adaptation design improve the reliability of the device under different speed and material conditions, and further ensures the balance correction accuracy.

[0026] Dustproof sealing rings are preferably installed on the inner sides of both ends of the sleeve 4, and the lip of the dustproof sealing ring is in interference contact with the outer wall of the rotating shaft 1.

[0027] In this embodiment, annular sealing grooves are provided on the inner sides of both ends of the sleeve 4. A dustproof sealing ring is installed in the sealing groove. The lip of the dustproof sealing ring extends toward the direction of the rotating shaft 1, and the lip is in interference contact with the outer wall of the rotating shaft 1. After assembly, the lip of the dustproof sealing ring is in a slightly compressed state. Select the appropriate dustproof sealing ring material according to the medium environment inside gearbox 2. If there is corrosive oil in gearbox 2, a sealing ring made of corrosion-resistant rubber can be selected. At the same time, a ring spring can be added in the sealing groove to enhance the fit between the sealing ring lip and the rotating shaft 1 through the preload of the spring. For working conditions with high dust concentration, a metal dustproof ring can be added to the outside of the sealing ring to form double sealing protection. It effectively prevents oil and dust from entering the sleeve 4 inside the gearbox 2, protecting the cleanliness of the internal precision transmission components and avoiding component wear and jamming caused by contaminants. The expanded material selection and double sealing structure improve the sealing reliability of the device in harsh environments and further extend the service life of core components such as the flexible wheel 7 and wave generator 9.

[0028] Preferably, the hysteresis rotor 12 has an annular structure, and a radial gap is left between the outer wall of the hysteresis rotor 12 and the inner wall of the sleeve 4.

[0029] In this embodiment, the hysteresis rotor 12 adopts a ring structure design. The inner wall of the ring hysteresis rotor 12 is fixedly connected to the end of the energy transfer cylinder 11. A uniform radial gap is reserved between the outer wall of the ring hysteresis rotor 12 and the inner wall of the sleeve 4, and the gap width remains consistent. Based on the magnetic field strength of the excitation coil stator 5 and the response sensitivity requirements of the hysteresis rotor 12, the thickness and radial dimensions of the annular hysteresis rotor 12 can be adjusted to enhance the magnetic field coupling efficiency. At the same time, the radial clearance can be designed for thermal expansion compensation according to the working temperature of the gearbox 2, reserving a larger clearance under high-temperature conditions to prevent the hysteresis rotor 12 from contacting the inner wall of the sleeve 4 due to thermal expansion. In addition, a magnetic conductive coating can be added to the surface of the annular hysteresis rotor 12 to further improve the magnetic field coupling effect. The ring structure makes the magnetic field coupling more uniform, improving the response sensitivity of the hysteresis rotor 12 to the magnetic field. The radial gap avoids contact friction between the hysteresis rotor 12 and the inner wall of the sleeve 4, reducing the operating noise and energy loss of the device. The thermal expansion compensation design and magnetic coating structure enable the device to adapt to complex working conditions such as high temperature and low magnetic field, improving the operating stability and magnetic field utilization efficiency.

[0030] The tooth profile of the rigid gear ring 6 is preferably an involute tooth profile, and the tooth profile of the flexible gear 7 is adapted to the tooth profile of the rigid gear ring 6.

[0031] In this implementation case, the tooth profile of the rigid gear ring 6 adopts the standard involute tooth profile, and the tooth profile parameters conform to the design standard of gear transmission. The tooth profile of the flexible gear 7 is fully matched with the involute tooth profile of the rigid gear ring 6, and the tooth flank clearance when the two mesh is kept within the preset range. Based on the transmission load requirements of the flexible gear 7 and the rigid gear ring 6, parameters such as the module and pressure angle of the involute tooth profile can be adjusted. For heavy-load conditions, a large module tooth profile can be selected to improve the load-bearing capacity. At the same time, a wear-resistant coating can be added to the tooth surface to reduce tooth surface wear during meshing. For high-speed transmission conditions, the tooth tip can be edge-modified to further reduce meshing impact and noise. In addition, the tooth flank clearance can be designed according to the working temperature to avoid tooth surface expansion at high temperatures, which could lead to jamming. The involute tooth meshing design makes the transmission process between the flexible gear 7 and the rigid gear ring 6 smoother, with less impact and lower noise, improving the operating comfort of the device. Parameter adjustment, wear-resistant coating and tooth tip trimming design enable the device to adapt to complex working conditions such as heavy load and high speed, extending the service life of the rigid gear ring 6 and the flexible gear 7 and improving the transmission reliability.

[0032] The preferred energy transfer cylinder 11 and wave generator 9 are formed by an integrated forging process.

[0033] In this implementation case, the energy transfer cylinder 11 and the wave generator 9 are formed by an integrated forging process. High-strength alloy materials are selected during forging, and the overall structure of the energy transfer cylinder 11 and the wave generator 9 is formed by one forging through a mold. No additional assembly process is required afterward, and it can be directly precision machined. Based on the load-bearing requirements of the device, alloy materials of different strength grades are selected. High-strength alloy steel is selected for high-torque conditions, while aluminum alloy is selected for lightweight applications and its strength is improved through strengthening treatment. At the same time, the integrated forging structure can be extended to a multi-segment integrated molding. When the energy transfer cylinder 11 is long, the integrated process of segmented forging and then overall splicing is used to reduce forging defects and improve the overall structure. In addition, reinforcing ribs can be added to the key stress-bearing parts of the integrated structure to further improve the structural rigidity. The assembly gaps between the separate parts were reduced, structural rigidity was improved, lag in power transmission was avoided, and precise transmission of angular deflection was ensured. Material selection and structural reinforcement design enabled the device to adapt to different torque and lightweight requirements, further improving the reliability and applicability of the device.

[0034] The excitation current of the stator 5 of the two sets of excitation coils is preferably output by an independent controller to adjust the angular deflection angle of the two wave generators 9 respectively, so as to realize the continuous stepless control of the relative angle between the two eccentric blocks 8.

[0035] In this implementation case, the two sets of excitation coil stators 5 are connected to independent controllers. The controllers can independently output different magnitudes of excitation current to the corresponding excitation coil stators 5 according to the unbalanced vibration signal of the rotating shaft 1. By adjusting the magnitude of the excitation current, the magnetic field strength generated by the excitation coil stators 5 is changed, thereby adjusting the angular deflection angle of the two wave generators 9 respectively. The controller can be an intelligent control module with an adaptive algorithm, which can automatically adjust the adjustment accuracy and response speed of the excitation current according to the speed change and vibration trend of the rotating shaft 1. At the same time, a current feedback detection unit can be added to monitor the current change of the excitation coil stator 5 in real time. When an abnormal current occurs, an alarm signal is issued in time and the system switches to the standby control mode. In addition, the independent controller can be expanded into a distributed control structure, which facilitates the coordinated work of multiple balancing devices and is suitable for balancing and correcting multi-axis gearboxes. The independent control of the dual stators enables the decoupled adjustment of the dual-wave generator 9, making the angle adjustment of the eccentric block 8 more flexible. Continuous stepless control can cover the full range of imbalance compensation. The intelligent control and distributed control design improves the control accuracy, fault tolerance and scalability of the device, and can adapt to the balance correction requirements of complex gearboxes such as multi-axis and variable speed gearboxes.

[0036] Preferably, an annular oil reservoir is provided on the inner wall of the sleeve 4 and at the root of the tooth of the gear ring 6, and the oil reservoir is filled with gear grease.

[0037] In this embodiment, an annular oil reservoir is provided on the inner wall of the sleeve 4 and at the tooth root of the rigid gear ring 6. The oil reservoir is distributed around the entire circumference of the rigid gear ring 6. The oil reservoir is filled with high-viscosity gear grease. The grease can slowly penetrate to the meshing part of the rigid gear ring 6 and the flexible gear 7 through capillary action. Based on the operating temperature and speed of gearbox 2, gear greases of different viscosity grades and temperature resistance can be selected. Meanwhile, tiny oil outlet holes can be opened at the bottom of the oil reservoir. The size of the outlet holes controls the penetration rate of the grease, preventing excessive or insufficient grease overflow. For long-term high-speed operation, a heat-conducting jacket can be added to the outside of the oil reservoir to reduce the rate of temperature rise of the grease and extend its service life. Furthermore, the volume of the oil reservoir can be designed according to the maintenance cycle requirements of the device, reducing the frequency of grease replenishment. This design can continuously provide lubrication to the meshing parts of the rigid gear ring 6 and the flexible gear 7, reducing tooth surface wear and extending the service life of the meshing pair. The selection of grease, control of the oil outlet hole and design of the heat-conducting sleeve enable the device to adapt to different operating conditions of different temperatures and speeds, further improving lubrication reliability and reducing maintenance costs.

[0038] The above embodiments are merely illustrative of the principles and effects of the present invention and are not intended to limit the invention. Any person skilled in the art can modify or alter the above embodiments without departing from the spirit and scope of the present invention. Therefore, all equivalent modifications or alterations made by those skilled in the art without departing from the spirit and technical concept disclosed in the present invention should still be covered by the claims of the present invention.

Claims

1. A gearbox balancing device, comprising a gearbox (2) on which a rotating shaft (1) is mounted, the rotating shaft (1) rotating within the gearbox (2) and transmitting power, characterized in that: The gearbox (2) is fixedly mounted with a base (3), and the base (3) is rotatably connected with a sleeve (4). The base (3) and the sleeve (4) are in a non-contact air gap fit. An excitation coil stator (5) is installed at the air gap fit position between the base (3) and the sleeve (4). The sleeve (4) is rigidly connected to the rotating shaft (1) via a flat key. A rigid wheel gear ring (6) is integrally formed and installed at the center of the sleeve (4). The rigid wheel gear ring (6) meshes with two flexible wheels (7). The number of teeth of the two flexible wheels (7) is two fewer than the number of teeth of the rigid wheel gear ring (6). The two flexible wheels (7) are distributed along the axial direction of the rotating shaft (1) with their cup mouths facing each other. An eccentric block (8) is fixedly installed on the outer side of the cup bottom of each of the two flexible wheels (7). A wave generator (9) is adapted to be installed inside each of the two flexible wheels (7). A bearing (10) is installed between the wave generator (9) and the rotating shaft (1). An energy transfer cylinder (11) is integrally connected to the inner ring of the wave generator (9). After the energy transfer cylinder (11) extends to the outer side of the cup bottom of the flexible wheel (7), a hysteresis rotor (12) is fixedly installed. The two sets of excitation coil stators (5) independently generate controllable rotating magnetic fields, which are coupled to the corresponding hysteresis rotors (12) through the air gap between the base (3) and the sleeve (4), driving the two wave generators (9) to deflect independently relative to the rotating shaft (1), thereby precisely controlling the relative angle between the two eccentric blocks (8) to synthesize a compensating centrifugal force that is equal in magnitude and opposite in direction to the unbalance of the rotating shaft (1).

2. The gearbox balancing device according to claim 1, characterized in that: A gap is left between the outer wall of the energy transfer cylinder (11) and the inner cavity wall of the flexible wheel (7), and the energy transfer cylinder (11) extends through the gap to the outer side of the bottom of the flexible wheel (7).

3. The gearbox balancing device according to claim 1, characterized in that: The eccentric block (8) has a fan-shaped structure, and the centroids of the two eccentric blocks (8) are located in a radially symmetrical position on the rotation axis (1).

4. The gearbox balancing correction device according to claim 1, characterized in that: The bearing (10) is a deep groove ball bearing. The inner ring of the deep groove ball bearing is interference-fitted with the rotating shaft (1), and the outer ring is interference-fitted with the inner hole of the wave generator (9).

5. A gearbox balancing device according to claim 1, characterized in that: Dustproof sealing rings are installed on the inner sides of both ends of the sleeve (4), and the lip of the dustproof sealing ring is in interference contact with the outer wall of the rotating shaft (1).

6. A gearbox balancing device according to claim 1, characterized in that: The hysteresis rotor (12) has an annular structure, and a radial gap is left between the outer wall of the hysteresis rotor (12) and the inner wall of the sleeve (4).

7. A gearbox balancing device according to claim 1, characterized in that: The tooth profile of the rigid wheel gear ring (6) is an involute tooth profile, and the tooth profile of the flexible wheel (7) is adapted to the tooth profile of the rigid wheel gear ring (6).

8. A gearbox balancing device according to claim 1, characterized in that: The energy transfer cylinder (11) and the wave generator (9) are formed by an integrated forging process.

9. A gearbox balancing device according to claim 1, characterized in that: The excitation current of the two sets of excitation coil stators (5) is output by an independent controller to adjust the angular deflection angle of the two wave generators (9) respectively, so as to realize the continuous stepless control of the relative angle between the two eccentric blocks (8).

10. A gearbox balancing device according to claim 1, characterized in that: The inner wall of the sleeve (4) and the root of the tooth of the gear ring (6) are provided with an annular oil reservoir, which is filled with gear grease.

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