Gear mesh excitation optimization method, gearbox abnormal noise optimization method and system

Abstract

The application discloses a gear meshing excitation optimization method, a gearbox abnormal sound optimization method and system. The gear meshing excitation optimization method comprises the following steps: running a target gear and a target shaft under a working condition m1, obtaining the maximum deformation of points A and B on the target shaft: Δ A , Δ B ; calculating the difference between Δ A and Δ B , and taking the absolute value of the difference as a deformation peak-peak value PPD (m1) ; step three: if PPD (m1) is zero, the method is ended, otherwise the diameter of a part of the target shaft is adjusted, the PPD (m1) of the target shaft after adjustment is reduced, and the purpose of optimizing the target gear meshing excitation is achieved. The gear meshing excitation is reduced by optimizing the shaft, and the vibration and noise performance of the gearbox is effectively improved.

Description

Technical Field

[0001] This invention relates to the field of gear meshing technology, specifically to a gear meshing excitation optimization method, a gearbox abnormal noise optimization method, and a system. Background Technology

[0002] The internal excitation of gear meshing transmission is a key factor causing gear vibration and noise. Current improvements in gearbox vibration and noise performance are mainly achieved through optimization of macroscopic and microscopic gear design parameters. Gear meshing excitation is the cause of gearbox vibration and noise problems, and the shaft on which the gears are located is also a participant in the meshing transmission, significantly influencing the gear meshing excitation. Specifically, during gear meshing, the meshing teeth are subjected to force along the normal direction of the tooth profile. When this meshing force is transmitted to the shaft, the axial deformation of the gear shaft varies due to differences in the resistance to deformation along the tooth width direction (e.g., the end closer to the bearing has stronger resistance). Therefore, improving gearbox vibration and noise performance solely by considering the optimization of macroscopic and microscopic gear design parameters is insufficient. A reasonable method is also needed to evaluate and optimize the influence of shaft-to-gear meshing excitation. Summary of the Invention

[0003] The technical problem to be solved by the present invention is to provide a method for optimizing gear meshing excitation, a method for optimizing gearbox noise, and a system for optimizing gear meshing excitation by optimizing the shaft.

[0004] To address the aforementioned technical problems, this invention provides a gear meshing excitation optimization method, comprising the following steps:

[0005] Step 1: Run the target gear and target shaft under operating condition m1, and obtain the maximum deformation at points A and B on the target shaft: , ;

[0006] Step 2: Calculation and The difference is recorded as the peak-to-peak value of the deformation, and the absolute value of this difference is denoted as the peak-to-peak value of the deformation. ;

[0007] Step 3: If If the value is zero, the method ends; otherwise, adjust the diameter of the target axis segment to make the adjusted target axis... This reduces the excitation level, thereby achieving the goal of optimizing the meshing excitation of the target gear.

[0008] The target gear is circumferentially fixed on the target shaft; the operating conditions of the target gear and the target shaft include m1, m2, m3..., with condition m1 being the target operating condition; points A and B are the two axial endpoints of the area on the target shaft that meshes with the target gear; the deformation direction is along the common normal direction of the target gear meshing.

[0009] Furthermore, in step three, the method for adjusting the diameter of the target shaft segment includes:

[0010] judge and The size of the target shaft is adjusted by increasing the diameter of the portion of the shaft segment on the side furthest from the target gear at the point corresponding to the larger one, and / or decreasing the diameter of the portion of the shaft segment on the side furthest from the target gear at the point corresponding to the smaller one.

[0011] Furthermore, in step three, the method for reducing the diameter of the target shaft segment includes:

[0012] Step a1: Based on the current structural design of the target shaft, determine the width and position of the shaft segment with reduced diameter;

[0013] Step a2: Based on the width and position of the reduced diameter shaft segment, perform fatigue durability design on the target shaft to determine the minimum adjustable diameter of the reduced diameter shaft segment;

[0014] Step a3: If the current diameter of the reduced diameter shaft segment is equal to the minimum adjustable diameter, the diameter of the target shaft segment cannot be reduced; if the current diameter of the reduced diameter shaft segment is greater than the minimum adjustable diameter, the adjusted diameter of the reduced diameter shaft segment is determined based on the minimum adjustable diameter of the reduced diameter shaft segment.

[0015] Furthermore, in step a3, determining the adjusted diameter of the reduced-diameter shaft segment includes:

[0016] Step b10: Extract n values ​​between the current diameter of the reduced diameter shaft segment and the minimum adjustable diameter to form n schemes for reducing the diameter of the target shaft segment, where n takes the values ​​5, 6, 7...; preferably, the n values ​​are evenly divided between the current diameter of the reduced diameter shaft segment and the minimum adjustable diameter.

[0017] Step b20: Obtain the peak-to-peak deformation value under working condition m1 for each scheme of reducing the diameter of the target shaft segment. ;

[0018] Step b30: Eliminate deformation peak value not less than The solution, in which, This is the first set value;

[0019] Step b40: Among the remaining options for reducing the diameter of the target shaft segment, select the option with the largest adjusted diameter as the final option.

[0020] Furthermore, after step b30, the following is also included:

[0021] Step b35: Sequentially obtain the peak-to-peak deformation values ​​for each scheme of reducing the diameter of the target shaft segment under working conditions m2, m3, m4... , , ...;

[0022] Step b36: Eliminate deformation peak value not less than The solution, in which, This is the second set value;

[0023] Furthermore, It is calculated by multiplying the working condition coefficient of working condition m1 by the target gear width.

[0024] To address the aforementioned technical problems, this invention provides a method for optimizing gearbox noise, comprising the following steps:

[0025] Step d1: Identify the meshing gear pair C that is causing abnormal noise in the gearbox, and take the driving gear and driving gear shaft of the gear pair C as the target gear and target shaft. Optimize the driving gear shaft using the gear meshing excitation optimization method as described in any one of claims 1-6.

[0026] Step d2: Check whether the abnormal noise of gear pair C meets the requirements when the gearbox is replaced with the optimized drive gear shaft under operating condition m1. If it does not meet the requirements, proceed to step c3; otherwise, end the method.

[0027] Step d3: Take the driven gear and driven gear shaft of gear pair C as the target gear and target shaft again, and use the gear meshing excitation optimization method as described in any one of claims 1-6 to optimize the driven gear shaft. During the optimization process, the gearbox replaces the optimized driving gear.

[0028] Among them, operating condition m1 is the operating condition when the gearbox produces abnormal noise.

[0029] To address the aforementioned technical problems, this invention provides a gearbox noise optimization system, comprising:

[0030] Active gear optimization module: used to optimize the active gear shaft by taking the active gear and active gear shaft of gear pair C as the target gear and target shaft, and using the gear meshing excitation optimization method as described in any one of claims 1-6.

[0031] The first inspection module is used to check whether the abnormal noise of gear pair C meets the requirements when the gearbox is replaced with the optimized drive gear shaft under working condition m1.

[0032] Driven gear optimization module: When the inspection result of the first inspection module is that the requirements are not met, the driven gear and driven gear shaft of gear pair C are re-designated as the target gear and target shaft, and the driven gear shaft is optimized using the gear meshing excitation optimization method as described in any one of claims 1-6. During the optimization process, the gearbox is replaced with the optimized driving gear.

[0033] Output module: Used to output the optimization results of the driving gear optimization module and the driven gear optimization module;

[0034] Among them, gear pair C is the meshing gear pair that produces abnormal noise in the gearbox.

[0035] Furthermore, the system also includes a second inspection module: used to inspect whether the abnormal noise of gear pair C under operating condition m1 meets the requirements when the optimized drive gear shaft and driven gear shaft are replaced in the gearbox.

[0036] Furthermore, the system also includes an output module: which is also used to output the verification results of the second verification module.

[0037] In summary, by employing the aforementioned gear meshing excitation optimization method, gearbox noise optimization method, and system, the gear meshing excitation is reduced through shaft optimization, effectively improving the vibration and noise performance of the gearbox. Attached Figure Description

[0038] In the attached diagram:

[0039] Figure 1 The image shows the simulated deformation curve of the target shaft before optimization in the gear meshing excitation optimization method of this invention.

[0040] Figure 2 The simulated deformation curve of the target shaft after optimization is shown in the gear meshing excitation optimization method of this invention.

[0041] Figure 3 This is a gearbox NVH simulation before and after optimization of the drive gear shaft in the gearbox noise optimization method of the present invention.

[0042] Figure 4 The target shaft structure dimension is the gearbox noise optimization method of the present invention. Detailed Implementation

[0043] The specific embodiments of the present invention will be further described below with reference to the accompanying drawings. It should be noted that these descriptions of the embodiments are for the purpose of helping to understand the present invention, but do not constitute a limitation thereof.

[0044] This invention discloses a gear meshing excitation optimization method, comprising steps S10 to S30. First, a parameter for evaluating the influence of the shaft on gear meshing is defined: the peak-to-peak value (PPD) of the shaft deformation along the gear tooth meshing direction on the tooth width length. Then, the shaft design is guided by reducing the PPD of the deformation. Addressing the current approach of primarily optimizing gear macroscopic and microscopic design parameters to reduce gear meshing excitation, this invention expands upon this method by providing a novel approach to reducing gear meshing excitation through shaft optimization, effectively promoting gear meshing excitation optimization and improving gearbox vibration and noise performance.

[0045] Since gear meshing transmission is part of the transmission system, the gear to be studied is first defined as the target gear, and the shaft on which the target gear is located is called the target shaft. The target gear is circumferentially fixed on the target shaft. The operating conditions of the target gear and the target shaft include m1, m2, m3... The main difference between each operating condition is the different speed and torque of the target gear. Operating condition m1 is the target operating condition, that is, a specific operating condition to be analyzed and studied.

[0046] Furthermore, we define points A and B as the two axial endpoints of the region on the target shaft that meshes with the target gear; and the deformation direction of the target shaft under study is along the common normal direction of the target gear meshing, that is, the direction of the meshing force experienced by the target gear and the target shaft as a whole during meshing, which can be simplified as the tooth normal direction. The following is an example... Figure 4 The target axis shown is described as the simulation target.

[0047] Step S10: Run the target gear and target shaft under operating condition m1, and obtain the maximum deformation at points A and B on the target shaft: , Optionally, simulation analysis can be used to simulate the operation of the target gear and the target shaft to obtain the deformation.

[0048] like Figure 1 As shown, this is the deformation curve of the target shaft on the meshing common normal. The horizontal axis represents the axial dimension of the target shaft, with point A as the zero point; the vertical axis represents the maximum deformation value at each corresponding point. Since the force on the target gear fluctuates within a certain range under certain operating conditions during gear meshing, the maximum deformation value at each point throughout the entire operation is taken as the analysis object. This simplifies the analysis process, facilitates data collection, and ensures that the deformation at each point on the target shaft reaches its maximum value simultaneously, at which point the force on the target gear is also at its maximum. Therefore, using the maximum deformation value for analysis is reasonable.

[0049] Step S20: Calculate and The difference is recorded as the peak-to-peak value of the deformation, and the absolute value of this difference is denoted as the peak-to-peak value of the deformation. ,Right now:

[0050]

[0051] Step S30: If If the value is zero, the method ends; otherwise, adjust the diameter of the target axis segment to make the adjusted target axis... This reduces the excitation level, thereby optimizing the meshing excitation of the target gear.

[0052] Optionally, in step three, the method for adjusting the diameter of the target shaft segment includes: determining... and The size of the target shaft is adjusted by increasing the diameter of the portion of the shaft segment on the side furthest from the target gear at the point corresponding to the larger one, and / or decreasing the diameter of the portion of the shaft segment on the side furthest from the target gear at the point corresponding to the smaller one.

[0053] By thickening the shaft diameter of the outer segment at the end with the larger maximum deformation, the deformation resistance of the target shaft at that end is increased, thereby reducing the deformation difference of the target shaft in the tooth width section and reducing the vibration and noise excitation of the target shaft on the gear meshing. Similarly, the deformation resistance of the target shaft at that end can also be reduced by thinning the shaft diameter of the outer segment at the end with the smaller maximum deformation, thus achieving the optimization purpose. The specific methods include the following two cases (1) and (2).

[0054] (1) If > ① Increase the diameter of the shaft segment on the side of point A furthest from the target gear, and / or ② decrease the diameter of the shaft segment on the side of point B furthest from the target gear. Adjustments ① and ② can be performed individually or simultaneously. Each adjustment method is described in detail below.

[0055] The target shaft is usually a rotating shaft, such as a common gearbox shaft, which needs to withstand bending moment and torque. Moreover, the target shaft is generally a stepped shaft, divided into different shaft segments depending on the parts mounted on the shaft and their functions. In this method, the shaft segments being adjusted are all the existing shaft segments that have already been designed in the target shaft. In order to achieve better adjustment results, the shaft segments that are closest to the target gear on both sides are usually adjusted. Therefore, methods ① and ② are as follows.

[0056] Since material removal is commonly used in machining and can save materials and reduce costs, the reduction method in step ② is a commonly used path, which will be described first.

[0057] ② Reduce the diameter of the shaft segment on the side of point B furthest from the target gear. The adjustment method includes steps a1 to a3.

[0058] Step a1: Based on the current structural design of the target shaft, determine the width and position of the reduced diameter shaft segment. As with the typical structural design of the target shaft described above, reduce the diameter of the nearest shaft segment on the side of the target shaft away from the target gear at point B. This determines both the position and width of the reduced diameter shaft segment.

[0059] like Figure 1 As shown, the target shaft is located on the side away from the target gear at point B. The nearest shaft segment is the groove segment between the target gear and a shaft shoulder, with a current diameter of 32.5 mm. The operating conditions m1 are set to 200 N·m and 3000 rpm. Simulation analysis yields the peak-to-peak value of the deformation. It is 15.74 μm.

[0060] Step a2: Based on the width and position of the reduced-diameter shaft segment, perform fatigue durability design on the target shaft to determine the minimum adjustable diameter of the reduced-diameter shaft segment. Based on the current dimensions of the target shaft, calculate the minimum diameter of the nearest shaft segment on the side furthest from point B from the target gear, provided that fatigue strength requirements are met. This minimum adjustable diameter is the minimum adjustable diameter of the reduced-diameter shaft segment.

[0061] Perform fatigue durability verification on the target axis, such as Figure 4 As shown, this is the fatigue durability check result when the shaft diameter of the groove section is 25mm. The horizontal axis is the axial dimension and the vertical axis is the fatigue safety factor. It is usually required that the fatigue safety factor be greater than 1. At this time, the fatigue safety factor at point B is 1.1, which means that the minimum adjustable diameter can be set to 25mm.

[0062] Step a3: If the current diameter of the reduced diameter shaft segment is greater than the minimum adjustable diameter, then determine the adjusted diameter of the reduced diameter shaft segment based on the minimum adjustable diameter of the reduced diameter shaft segment. The specific determination method is as follows: steps b10~b40.

[0063] Step b10: Between the current diameter of the reduced diameter shaft segment and the minimum adjustable diameter, extract n values ​​to form n possible schemes for reducing the diameter of the target shaft segment, where n takes the values ​​5, 6, 7, ... The value of n varies depending on the size of the interval between the current diameter of the reduced diameter shaft segment and the minimum adjustable diameter.

[0064] Optionally, between the current diameter of the reduced diameter shaft segment and the minimum adjustable diameter, n values ​​are evenly divided to form n schemes for reducing the diameter of the target shaft segment. To facilitate calculation and design, the n evenly spaced values ​​can be rounded to form n schemes.

[0065] In addition, when the interval between the current diameter of the reduced diameter shaft segment and the minimum adjustable diameter is greater than 6mm, n schemes for reducing the diameter of the target shaft segment can be formed with intervals of 1mm and / or 0.5mm.

[0066] As shown in Table 1, in order to simplify the calculation, eight values ​​are taken between 32.5 and 25 mm: 32 mm, 31 mm...26 mm, 25 mm, corresponding to eight schemes.

[0067] Step b20: Obtain the peak-to-peak deformation value under working condition m1 for each scheme of reducing the diameter of the target shaft segment. The values ​​are shown in the second column of Table 1.

[0068] Step b30: Eliminate deformation peak value not less than The solution.

[0069] in, The first set value, It is obtained by multiplying the working condition coefficient of working condition m1 and the target gear width. The calculation formula is as follows:

[0070]

[0071] Working condition m1 is the target working condition with a working condition coefficient of 0.00025, and D is the target gear width.

[0072] Depend on Figure 4 It can be seen that the target gear width D is equal to 42.5mm, therefore Therefore, the four options of 32mm, 31mm, 30mm and 29mm were eliminated.

[0073] Optionally, the current working condition m1 is only a specific working condition for the target shaft and target gear to operate, while the target shaft and target gear will also operate under other working conditions. Therefore, other working conditions are needed to help determine the final adjustment scheme, as shown in steps b35 and b36.

[0074] Step b35: Sequentially obtain the peak-to-peak deformation values ​​for each scheme of reducing the diameter of the target shaft segment under working conditions m2, m3, m4... , , ...As shown in the third and fourth columns of Table 1.

[0075] Step b36: Eliminate deformation peak value not less than The solution.

[0076] in, This is the second set value. It is obtained by multiplying the working condition coefficient (other than working condition m1) by the target gear width. The calculation formula is as follows:

[0077]

[0078] Other operating conditions are non-target operating conditions and are less important than the target operating condition m1; therefore, the operating condition coefficient for other operating conditions is 0.0005. Calculations show that there are no remaining technical solutions that need to be eliminated.

[0079] Step b40: Among the remaining options for reducing the diameter of the target shaft segment, select the option with the largest adjusted diameter as the final option. Considering the overall strength of the entire target shaft, the option with the largest shaft diameter is chosen as the final option. For example... Figure 2 As shown, after reducing the diameter of the groove section to 28mm, the peak-to-peak value of the deformation under working condition m1 is... It is 9.82 μm.

[0080] Table 1. PPD values ​​of the scheme for reducing the diameter of a portion of the target shaft under different working conditions.

[0081] 32.5mm 15.74 25.10 -11.22 32mm 14.70 24.06 -12.22 31mm 13.63 22.95 -13.22 30mm 12.54 21.83 -14.23 29mm 11.44 20.69 -15.23 28mm 9.82 19.52 -16.23 27mm 9.18 18.33 -17.23 26mm 7.01 16.09 -19.24 25mm 5.81 14.81 -20.24 Target (absolute value) ≤10 ≤20 ≤20

[0082] Additionally, at the beginning of step a3, if the current diameter of the reduced diameter shaft segment is equal to the minimum adjustable diameter, the diameter of the target shaft segment cannot be reduced. Since there is no adjustable space, this path cannot be optimized. Try using other paths, such as returning to path ①. If path ① also cannot be optimized, then the method ends. It is impossible to optimize the meshing excitation of the target gear by optimizing the target shaft. This situation is almost impossible.

[0083] Additionally, at the beginning of step a3, if the current diameter of the reduced diameter shaft segment is equal to the minimum adjustable diameter, the diameter of the target shaft segment cannot be reduced. Since there is no adjustable space, this path cannot be optimized. Try using other paths, such as returning to path ①. If path ① also cannot be optimized, then the method ends. It is impossible to optimize the meshing excitation of the target gear by optimizing the target shaft. This situation is extremely rare.

[0084] For the other path: ① Increase the diameter of the shaft segment on the side of point A furthest from the target gear. The process is similar to ②, except that the method involves increasing the shaft segment diameter. Specifically, the steps are as follows: .

[0085] step Based on the current structural design of the target shaft, determine the width, position, and maximum adjustable diameter of the shaft segment to be enlarged. As with the typical structural design of the target shaft described above, on the side of the target shaft furthest from the target gear at point A, enlarge the diameter of the nearest shaft segment. This determines the position and width of the shaft segment to be enlarged. However, due to the installation structure of stepped shafts, there is usually a maximum limit, which is the maximum adjustable diameter.

[0086] step If the current diameter of the enlarged diameter shaft segment is less than the maximum adjustable diameter, then the adjusted diameter of the enlarged diameter shaft segment is determined based on the maximum adjustable diameter of the enlarged diameter shaft segment. The specific determination method is as follows: ~ .

[0087] step Between the current diameter of the shaft segment to be enlarged and the maximum adjustable diameter, n values ​​are extracted to form n possible schemes for increasing the diameter of the target shaft segment, where n takes the values ​​5, 6, 7, ... The value of n varies depending on the size of the interval between the current diameter of the shaft segment to be enlarged and the maximum adjustable diameter.

[0088] step : Obtain the peak-to-peak deformation value under working condition m1 for each scheme of increasing the diameter of the target shaft section. .

[0089] step The peak-to-peak value of the eliminated deformation amount is not less than The solution.

[0090] in, The first set value, It is obtained by multiplying the working condition coefficient of working condition m1 and the target gear width. The calculation formula is as follows:

[0091]

[0092] Working condition m1 is the target working condition with a working condition coefficient of 0.00025, and D is the target gear width.

[0093] Step b35: Sequentially obtain the peak-to-peak deformation values ​​for each scheme of increasing the diameter of the target shaft segment under working conditions m2, m3, m4... , , ...

[0094] Step b36: Eliminate deformation peak value not less than The solution.

[0095] in, This is the second set value. It is obtained by multiplying the working condition coefficient (other than working condition m1) by the target gear width. The calculation formula is as follows:

[0096]

[0097] Other operating conditions are non-target operating conditions and are less important than the target operating condition m1. Therefore, the operating condition coefficient for other operating conditions is 0.0005.

[0098] Step b40: Among the remaining options for increasing the diameter of the target shaft segment, select the option with the smallest adjusted diameter as the final option. Considering the overall cost of the entire target shaft, the option with the smallest shaft diameter is selected as the final option.

[0099] In addition, in the steps Initially, if the current diameter of the increased diameter shaft segment is equal to the maximum adjustable diameter, the diameter of the target shaft segment cannot be increased. Since there is no adjustable space, this path cannot be optimized. Try using other paths, such as returning to path ②. If path ② also cannot be optimized, then the method ends. It is impossible to optimize the meshing excitation of the target gear by optimizing the target shaft. This situation is extremely rare.

[0100] (2) If < There are also two methods: reduce the diameter of the shaft segment on the side of point A furthest from the target gear, and / or increase the diameter of the shaft segment on the side of point B furthest from the target gear. The specific process of increasing or decreasing the diameter of the shaft segment is similar to that described above and will not be detailed further.

[0101] This invention discloses a method for optimizing abnormal noise in a gearbox, comprising the following steps d1 to d3: utilizing the aforementioned gear meshing excitation optimization method, the meshing gears that generate abnormal noise are optimized, thereby reducing the abnormal noise. For example, a gearbox exhibits a significant gear squealing problem in the primary gear pair within the torque range of 200 N·m and a speed range of 1500–3500 rpm.

[0102] Step d1: Identify the meshing gear pair C that is causing the abnormal noise in the gearbox, and take the driving gear and its shaft as the target gear and shaft. Use the gear meshing excitation optimization method described above to optimize the driving gear shaft. Since the bearing where the driven gear is located experiences greater torque, a slotting method may be used during optimization; therefore, optimization should be prioritized on the driving gear and shaft. Figure 4 The target shaft shown is the driving gear shaft of gear pair C.

[0103] Using the MASTA software simulation, the deformation curve of the shaft containing the driving tooth of the first-stage gear pair in the tooth normal direction was confirmed as follows: Figure 1 As shown, the curve shows a decreasing trend from left to right in terms of tooth width, and the peak value of deformation PPD is 15.74 mm. Point A is on the left and point B is on the right.

[0104] Operating condition m1 is the operating condition of the first-stage gear pair when the gearbox produces abnormal noise, that is, the gearbox operates at a torque of 200 N·m and a speed of 3000 rpm to reach the operating condition m1 of the target gear.

[0105] like Figure 2 As shown, after reducing the diameter of the groove section to 28mm, the peak-to-peak value of the deformation under working condition m1 is... It is 9.82 μm.

[0106] Step d2: Check if the optimized drive gear shaft replaces the gearbox and runs the gear pair C under operating condition m1 to check if the abnormal noise meets the requirements. If not, proceed to step c3; otherwise, end the method. After optimizing the drive gear shaft, verify the optimization effect. If the abnormal noise can be reduced to the required value, the objective is achieved, and further optimization can be stopped. If the abnormal noise is not reduced to the required value, proceed to step d3 to continue optimizing the driven gear and driven gear shaft. Optimize both the drive and driven ends simultaneously to maximize the optimization of the shaft-gear meshing excitation.

[0107] like Figure 3 As shown, the gearbox NVH simulation before and after optimization of the drive gear shaft shows an overall improvement of 5dB under operating condition m1.

[0108] Step d3: Retake the driven gear and driven gear shaft of gear pair C as the target gear and target shaft, and use the gear meshing excitation optimization method described above to optimize the driven gear shaft. During the optimization process, the gearbox is replaced with the optimized driving gear.

[0109] This invention discloses a gearbox noise optimization system, comprising: a driving gear optimization module: used to optimize the driving gear and driving gear shaft of gear pair C as the target gear and target shaft, and using the aforementioned gear meshing excitation optimization method to optimize the driving gear shaft; a first verification module: used to verify whether the gearbox, when replaced with the optimized driving gear shaft, meets the requirements for the noise of gear pair C under operating condition m1; a driven gear optimization module: used to re-designate the driven gear and driven gear shaft of gear pair C as the target gear and target shaft when the verification result of the first verification module is not met, and to optimize the driven gear shaft using the aforementioned gear meshing excitation optimization method, wherein the gearbox is replaced with the optimized driving gear during the optimization process; and an output module: used to output the optimization results of the driving gear optimization module and the driven gear optimization module; wherein, gear pair C is the meshing gear pair in the gearbox that generates noise.

[0110] Optionally, the system also includes a second inspection module: used to inspect whether the abnormal noise of gear pair C under operating condition m1 meets the requirements when the gearbox is replaced with the optimized drive gear shaft and driven gear shaft.

[0111] Optionally, the system also includes an output module: which is also used to output the verification results of the second verification module.

[0112] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention and not to limit its scope of protection. Although the present invention has been described in detail with reference to the above embodiments, those skilled in the art should understand that after reading the present invention, they can still make various changes, modifications or equivalent substitutions to the specific implementation of the invention, but these changes, modifications or equivalent substitutions are all within the scope of protection of the pending claims of the invention.

Claims

1. A method for optimizing gear meshing excitation, characterized in that, The steps include the following: Step 1: Run the target gear and target shaft under operating condition m1, and obtain the maximum deformation at points A and B on the target shaft: , ; Step 2: Calculation and The difference is recorded as the peak-to-peak value of the deformation, and the absolute value of this difference is denoted as the peak-to-peak value of the deformation. ; Step 3: If If the value is zero, the method ends; otherwise, adjust the diameter of the target axis segment to make the adjusted target axis... Decrease; The target gear is circumferentially fixed on the target shaft; the operating conditions of the target gear and the target shaft include m1, m2, m3..., with condition m1 being the target operating condition; points A and B are the two axial endpoints of the area on the target shaft that meshes with the target gear; the deformation direction is along the common normal direction of the target gear meshing. In step three, the method for adjusting the diameter of the target shaft segment includes: judge and The size of the target shaft is adjusted by increasing the diameter of the portion of the shaft segment on the side furthest from the target gear at the point corresponding to the larger one, and / or decreasing the diameter of the portion of the shaft segment on the side furthest from the target gear at the point corresponding to the smaller one.

2. The gear meshing excitation optimization method according to claim 1, characterized in that, In step three, the method for reducing the diameter of the target shaft segment includes: Step a1: Based on the current structural design of the target shaft, determine the width and position of the shaft segment with reduced diameter; Step a2: Based on the width and position of the reduced diameter shaft segment, perform fatigue durability design on the target shaft to determine the minimum adjustable diameter of the reduced diameter shaft segment; Step a3: If the current diameter of the reduced diameter shaft segment is equal to the minimum adjustable diameter, the diameter of the target shaft segment cannot be reduced; if the current diameter of the reduced diameter shaft segment is greater than the minimum adjustable diameter, the adjusted diameter of the reduced diameter shaft segment is determined based on the minimum adjustable diameter of the reduced diameter shaft segment.

3. The gear meshing excitation optimization method according to claim 2, characterized in that, In step a3, determining the adjusted diameter of the reduced diameter shaft segment includes: Step b10: Between the current diameter of the reduced diameter shaft segment and the minimum adjustable diameter, extract n values ​​to form n schemes for reducing the diameter of the target shaft segment, where n takes the values ​​5, 6, 7...; Step b20: Obtain the peak-to-peak deformation value under working condition m1 for each scheme of reducing the diameter of the target shaft segment. ; Step b30: Eliminate deformation with a peak-to-peak value not less than The solution, in which, This is the first set value; Step b40: Among the remaining options for reducing the diameter of the target shaft segment, select the option with the largest adjusted diameter as the final option; It is calculated by multiplying the working condition coefficient of working condition m1 by the target gear width.

4. The gear meshing excitation optimization method according to claim 3, characterized in that, The process includes the following after step b30: Step b35: Sequentially obtain the peak-to-peak deformation values ​​for each scheme of reducing the diameter of the target shaft segment under working conditions m2, m3, m4... , , ...; Step b36: Eliminate deformation peak value not less than The solution, in which, This is the second set value. It is calculated by multiplying the working condition coefficients of working conditions other than working condition m1 with the target gear width.

5. A method for optimizing abnormal noise in a gearbox, characterized in that, The steps include the following: Step d1: Identify the meshing gear pair C that is causing abnormal noise in the gearbox, and take the driving gear and driving gear shaft of the gear pair C as the target gear and target shaft. Optimize the driving gear shaft using the gear meshing excitation optimization method as described in any one of claims 1-4. Step d2: Check whether the abnormal noise of gear pair C meets the requirements when the gearbox is replaced with the optimized drive gear shaft under operating condition m1. If it does not meet the requirements, proceed to step c3; otherwise, end the method. Step d3: Take the driven gear and driven gear shaft of gear pair C as the target gear and target shaft again, and use the gear meshing excitation optimization method as described in any one of claims 1-4 to optimize the driven gear shaft. During the optimization process, the gearbox replaces the optimized driving gear. Among them, operating condition m1 is the operating condition when the gearbox produces abnormal noise.

6. A gearbox noise optimization system, characterized in that, include: Active gear optimization module: used to optimize the active gear shaft of gear pair C by taking the active gear and the active gear shaft as the target gear and target shaft, and using the gear meshing excitation optimization method as described in any one of claims 1-4. The first inspection module is used to inspect whether the abnormal noise of gear pair C meets the requirements when the gearbox is replaced with the optimized drive gear shaft under working condition m1. Driven gear optimization module: When the inspection result of the first inspection module is that the requirements are not met, the driven gear and driven gear shaft of gear pair C are re-designated as the target gear and target shaft, and the driven gear shaft is optimized using the gear meshing excitation optimization method as described in any one of claims 1-4. During the optimization process, the gearbox is replaced with the optimized driving gear. Output module: Used to output the optimization results of the driving gear optimization module and the driven gear optimization module; Among them, gear pair C is the meshing gear pair that produces abnormal noise in the gearbox.

7. A gearbox noise optimization system according to claim 6, characterized in that, Also includes: The second inspection module is used to inspect whether the abnormal noise of gear pair C under operating condition m1 is met when the optimized drive gear shaft and driven gear shaft of the gearbox are replaced.

8. A gearbox noise optimization system according to claim 7, characterized in that, Also includes: The output module is also used to output the verification results of the second verification module.

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