Rack and method for simulating influence of transmission shaft on vibration noise and fatigue of transmission

Abstract

The invention belongs to the field of transmissions, and discloses a rack and method for simulating the vibration noise and fatigue influence of a transmission shaft on a transmission, the device comprises a bottom plate, the bottom plate is fixedly connected with a driving motor support, a bearing seat adjusting plate and a motor support adjusting plate which are connected in sequence, the upper end of the driving motor support is fixedly connected with a driving motor, and the lower end of the driving motor is fixedly connected with a bearing seat adjusting plate. A first adjusting unit capable of moving front and back is arranged on the bearing seat adjusting plate, a second adjusting unit capable of moving front and back is arranged on the motor support adjusting plate, the driving motor is rotationally connected with the first adjusting unit through a transmission shaft, and the first adjusting unit is rotationally connected with the second adjusting unit through a transition shaft. A balance weight is arranged at one end, close to the first adjusting unit, of the transmission shaft, the transmission shaft is sleeved with the balance weight, relative positions of all components are flexibly adjusted through the first adjusting unit and the second adjusting unit which can move front and back, different installation states are simulated, and the unbalance amount of the transmission shaft is accurately adjusted through the balance weight.

Description

TECHNICAL FIELD

[0001] The application belongs to the technical field of transmission and relates to a bench and method for simulating the influence of a transmission shaft on the vibration noise and fatigue of a transmission. BACKGROUND

[0002] During vehicle driving, the transmission system is the core part of power supply, and the performance directly affects the overall performance of the vehicle. The whole vehicle transmission system is composed of key components such as engine, clutch, transmission, transmission shaft, rear axle, etc. If the matching is improper, it will cause serious fatigue life problems and noise, vibration and roughness problems, which seriously affect the driving quality and service life of the vehicle.

[0003] As the core component of the transmission system, the transmission bears the important task of reducing the output torque of the engine and transmitting it to the rear end transmission shaft and rear axle. The rear end is usually connected with the transmission shaft through the output flange, and the two work together under the condition of high speed and large torque. The rotational unbalance of the transmission shaft and the installation equivalent angle are the key parameters for matching the two. When the rotational unbalance of the transmission shaft is too large, the first-order vibration of the transmission shaft rotation frequency will increase significantly, and then the alternating load on the transmission assembly will be generated. If the first-order bending mode of the transmission shaft or the transmission system is excited to resonate, the transmission will quickly crack the shell and break the bolt. When the installation equivalent angle of the transmission shaft is too large, the second-order torque fluctuation and speed fluctuation of the transmission shaft will be generated, which will cause the reciprocal knocking of the internal gears of the transmission and cause knocking noise.

[0004] In order to meet the diversified market demand, the main plant replaces different parameters of engine, transmission, transmission shaft, rear axle and other components on the same platform to obtain various vehicle configurations, but ignores the change of the dynamic characteristics of the transmission system after matching different components. SUMMARY

[0005] In view of the deficiencies in the prior art, the purpose of the present application is to provide a bench and method for simulating the influence of a transmission shaft on the vibration noise and fatigue of a transmission, which can simulate the influence of the unbalance amount and the installation equivalent angle of the transmission shaft on the vibration noise and fatigue life of the transmission under the whole vehicle working condition, and obtain the matching requirements of the transmission for the transmission shaft.

[0006] In order to achieve the above purpose, the present application adopts the following technical scheme: The present application provides a bench for simulating the influence of transmission shaft on transmission vibration noise and fatigue, comprising a base plate, a driving motor support, a bearing seat adjusting plate and a motor support adjusting plate connected in sequence are fixedly connected on the base plate, a driving motor is fixedly connected on the upper end of the driving motor support, a first adjusting unit moving forward and backward is arranged on the bearing seat adjusting plate, a second adjusting unit moving forward and backward is arranged on the motor support adjusting plate, the first adjusting unit and the bearing seat adjusting plate and the second adjusting unit and the motor support adjusting plate are fixedly connected through connecting pieces, the driving motor is rotatably connected with the first adjusting unit through a transmission shaft, the first adjusting unit is rotatably connected with the second adjusting unit through a transition shaft, a balance weight is arranged on one end of the transmission shaft close to the first adjusting unit and is sleeved on the transmission shaft.

[0007] Further, a first flexible coupling is arranged on the output end of the driving motor, one end of the first flexible coupling is rotatably connected with the output shaft of the driving motor through the driving motor bearing seat, and the other end is rotatably connected with the transmission assembly through the transmission support.

[0008] Further, a groove is arranged on the upper end of the bearing seat adjusting plate, the first adjusting unit comprises a transition bearing seat installed on the upper end of the bearing seat adjusting plate and a speed measuring fluted disc installed on the transition shaft, and the connecting pieces pass through the transition bearing seat from top to bottom to fixedly connect the transition bearing seat with the bearing seat adjusting plate.

[0009] Further, the second adjusting unit comprises a load motor support, a load motor and a load motor bearing seat installed on the upper end of the motor support adjusting plate, a transition shaft, an inertia disc and an installation shaft are arranged in sequence on the side of the transition bearing seat away from the transmission shaft, one end of a second flexible coupling is sleeved on the installation shaft, and the other end is connected with the output shaft of the load motor through the load motor bearing seat.

[0010] Further, a vibration acceleration sensor is arranged on the transmission assembly shell, the vibration acceleration sensor is connected with a signal conditioner, is used for measuring the vibration of the transmission assembly, the signal conditioner is also connected with a sound sensor and a speed sensor, the sound sensor is used for measuring the noise of the transmission assembly, and the speed sensor obtains the speed of the transmission shaft through the speed measuring fluted disc.

[0011] Further, the inertia disc is used for simulating the inertia of the whole vehicle, a plurality of dynamic balance holes are arranged on the inertia disc in the circumferential direction, the dynamic balance holes are uniformly distributed in the circumferential direction, and the central angle between adjacent two holes is 15°.

[0012] The present application also provides a method for simulating the influence of transmission shaft on transmission vibration noise and fatigue, based on the above-mentioned bench for simulating the influence of transmission shaft on transmission vibration noise and fatigue, comprising the following steps: adjusting the unbalance amount of the transmission shaft by installing balance weights with different masses , the equivalent angle of the transmission shaft is adjusted by the first adjustment unit and the second adjustment unit ; For unbalanced and the equivalent angle Combine to get different combination incentives ; Establish a dynamic simulation model and obtain the target fatigue life based on simulation and experimental results Fatigue excitation boundary under ; Based on different combination incentives The sound signal , get the acoustic excitation boundary ; According to the fatigue excitation boundary Harmonic excitation boundary Obtaining the imbalance and the equivalent angle The minimum value of .

[0013] Furthermore, the imbalance for:

[0014] in, , is the maximum number of test groups for imbalance, The imbalance of the gantry drive shaft under the balance quality level G16.

[0015] Furthermore, the equivalent angle for:

[0016] in, is the index of the size of the equivalent angle of each group, is the number of centering holes moved relative to the initial position at the maximum equivalent angle, is the centering hole spacing, is the maximum number of test groups of equivalent angle and is an odd number. It is the distance between the rightmost end of the transmission and the leftmost end of the bearing support.

[0017] Furthermore, the number of the centering holes moved relative to the initial position at the maximum equivalent angle is :

[0018] in, Round down, is the centering hole spacing.

[0019] Compared with the prior art, the present invention has the following beneficial technical effects: The application is a bench for simulating the influence of a transmission shaft on transmission vibration fatigue and noise, which can simulate the equivalent included angle under different installation conditions by flexibly and quickly adjusting the relative positions of various components through the first and second adjustment units which can move synchronously forward and backward.

[0020] The application is a bench for simulating the influence of a transmission shaft on transmission vibration noise and fatigue, which can simulate the influence of a transmission shaft on transmission vibration noise and fatigue under whole vehicle working conditions, has low cost and is convenient to operate.

[0021] The application is a bench for simulating the influence of a transmission shaft on transmission vibration noise and fatigue, which is provided with a balance hole on the inertia disc to avoid introducing new unbalance and ensure the accuracy of test results.

[0022] The application is a bench for simulating the influence of a transmission shaft on transmission vibration noise and fatigue, which can simulate various vehicle models such as a tractor and a mine truck by adjusting the inertia of different inertia discs and the type of the transmission shaft, and has a wide application range.

[0023] The application is a method for simulating the influence of a transmission shaft on transmission vibration noise and fatigue, which controls the unbalance of the transmission shaft and the equivalent included angle of the transmission shaft through a bench, tests the vibration and noise data of the transmission assembly, combines the vibration fatigue simulation and subjective evaluation results, and obtains the quantitative matching requirements of the unbalance and the equivalent included angle of the transmission shaft when the transmission assembly is matched, thereby improving the reliability of the transmission assembly and the comfort of the whole vehicle.

[0024] The application is a method for simulating the influence of a transmission shaft on transmission vibration noise and fatigue, which compares and analyzes the actual data collected during the experiment with the data obtained through simulation, ensures that the simulation dynamics model can accurately reflect the actual situation, combines the experimental test with simulation, avoids multiple fatigue tests, and greatly reduces the time cost and material cost.

[0025] The application is a method for simulating the influence of a transmission shaft on transmission vibration noise and fatigue, which determines the acoustic excitation boundary by using the noise test data to perform subjective evaluation , which is more in line with the driving experience of the driver during use and has stronger reference value. The subjective evaluation team fully considers the industry characteristics of commercial vehicle drivers in terms of age and gender, and the obtained acoustic excitation boundary is more accurate. BRIEF DESCRIPTION OF DRAWINGS

[0026] Figure 1 It is a structural schematic diagram of the bench for simulating the influence of a transmission shaft on transmission vibration noise and fatigue according to the application; Figure 2 It is a structural schematic diagram of the installation of a vibration acceleration sensor in the embodiment of the application; Figure 3 It is a structural schematic diagram of a bearing seat adjustment plate in the embodiment of the application; Figure 4 Schematic diagram of the structure of the transition bearing seat in an embodiment of the present invention; Figure 5 The present invention is a flow chart of a method for simulating the influence of a transmission shaft on transmission vibration, noise and fatigue.

[0027] Reference numerals: 1-drive motor; 2-drive motor bearing seat; 3-first flexible coupling; 4-drive motor support; 5-transmission support; 6-transmission assembly; 7-drive shaft; 8-balance weight; 9-speed measuring gear disc; 10-transition bearing seat; 11-bearing seat adjustment plate; 12-transition shaft; 13-inertia disk; 14-mounting shaft; 15-second flexible coupling; 16-load motor bearing seat; 17-load motor; 18-load motor support; 19-motor support adjustment plate; 20-base plate; 21-acoustic sensor; 22-vibration acceleration sensor; 23-speed sensor; 24-signal conditioner. DETAILED DESCRIPTION

[0028] In order to enable those skilled in the art to better understand the solutions of the present invention, the technical solutions in the embodiments of the present invention will be clearly and completely described below in conjunction with the drawings in the embodiments of the present invention. Obviously, the embodiments described are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without making creative efforts should fall within the scope of protection of the present invention.

[0029] Example 1 The present invention provides a test bench for simulating the influence of the transmission shaft on the vibration, noise and fatigue of the transmission. Figure 1 As shown, it includes: a base plate 20, on which a drive motor support 4, a bearing seat adjustment plate 11 and a motor support adjustment plate 19 connected in sequence are fixedly connected, the upper end of the drive motor support 4 is fixedly connected to the drive motor 1, the bearing seat adjustment plate 11 is provided with a first adjustment unit that moves forward and backward, and the motor support adjustment plate 19 is provided with a second adjustment unit that moves forward and backward, the first adjustment unit and the bearing seat adjustment plate 11 and the second adjustment unit and the motor support adjustment plate 19 are fixedly connected by connecting members, the drive motor 1 is rotatably connected to the first adjustment unit through the transmission shaft 7, the first adjustment unit is rotatably connected to the second adjustment unit through the transition shaft 12, and a balancing weight 8 is provided on one end of the transmission shaft 7 near the first adjustment unit, which is sleeved on the transmission shaft 7.

[0030] Specifically, the driving motor support 4, the bearing seat adjusting plate 11 and the motor support adjusting plate 19 are sequentially arranged on the bottom plate 20 from left to right, and are fixedly connected with the bottom plate 20 respectively. The upper end of the driving motor support 4 is provided with the driving motor 1 and the driving motor bearing seat 2, one end of the first flexible coupling 3 is fixedly connected with the output shaft of the driving motor 1 through the driving motor bearing seat 2, and the other end is fixedly connected with the transmission assembly 6 through the transmission support 5, and the transmission support 5 is fixedly connected with the bottom plate 20 at the lower end.

[0031] The first adjusting unit comprises the transition bearing seat 10 mounted on the upper end of the bearing seat adjusting plate 11 and the speed measuring fluted disc 9 mounted on the transition shaft 12. The connecting piece passes through the transition bearing seat 10 from top to bottom, and fixedly connects the transition bearing seat 10 with the bearing seat adjusting plate 11. In the embodiment, the connecting piece is a bolt. The transmission shaft 7 is arranged between the transmission assembly 6 and the speed measuring fluted disc 10, and the balance weight 8 is sleeved on the side of the transmission shaft 7 close to the speed measuring fluted disc 9. In the embodiment, the balance weight 8 is in a circular arc structure, and the inner diameter is the same as the outer diameter of the transmission shaft 7. The unbalance amount of the transmission shaft 7 is adjusted by replacing the balance weight 8 with different mass.

[0032] The bearing seat adjusting plate 11 is fixedly mounted on the bottom plate 20, as shown in Figure 3 The bearing seat adjusting plate 11 is provided with parallel grooves, specifically T-shaped grooves, on the upper end. The transition bearing seat 10 can move forward and backward along the T-shaped grooves, and is fixedly connected with the bearing seat adjusting plate 11 by bolts when moved to the required position.

[0033] The second adjusting unit comprises the load motor support 18 and the load motor 17 mounted on the upper end of the motor support adjusting plate 19. The transition bearing seat 10 is sequentially provided with the transition shaft 12, the inertia disc 13 and the mounting shaft 14 away from the side of the transmission shaft 7. One end of the second flexible coupling 15 is sleeved on the mounting shaft 14, and the other end is connected with the output shaft of the load motor 17 through the load motor bearing seat 16. The motor support adjusting plate 19 is fixedly mounted on the bottom plate 20, and the upper end is also provided with parallel grooves, specifically T-shaped grooves, for forward and backward movement. The inertia disc 13 is used for simulating the inertia of the whole vehicle, and the dynamic balance holes are uniformly distributed on the two side end faces at intervals of 15°, which are used for the installation of balance screws and balance washers to ensure the dynamic balance of the inertia disc 13.

[0034] By adjusting the inertia size of different inertia discs 13 and the model of the transmission shaft 7, various vehicle models such as a tractor and a mine truck can be simulated.

[0035] As shown in Figure 2As shown, a vibration acceleration sensor 22 is mounted on the housing of the transmission assembly 6. This sensor is connected to a signal conditioner 24 for measuring the vibration of the transmission assembly 6. The signal conditioner 24 is also connected to an acoustic sensor 21 and a speed sensor 23. The acoustic sensor 21 measures the noise of the transmission assembly 6, while the speed sensor 23 obtains the transmission shaft speed via the speed measuring sprocket 9. The vibration acceleration sensor 22 is mounted on the housing of the transmission assembly 6 to measure vibration; the acoustic sensor 21 is positioned near the transmission assembly 6 to measure noise; and the signal conditioner 24 processes test signals, with the sampling rate of each channel being no less than 10240 Hz.

[0036] Example 2 A method for simulating the effect of transmission shaft on transmission vibration, noise and fatigue, such as Figure 4 As shown, the following steps are included: adjusting the unbalance of the transmission shaft 7 by installing balancing weights 8 of different masses , adjust the equivalent angle of the transmission shaft 7 through the first adjustment unit and the second adjustment unit ; For unbalanced and the equivalent angle Combine to get different combination incentives ; Establish a dynamic simulation model and obtain the target fatigue life based on simulation and experimental results Fatigue excitation boundary under ; Based on different combination incentives The sound signal , get the acoustic excitation boundary ; According to the fatigue excitation boundary Harmonic excitation boundary Obtaining the imbalance and the equivalent angle The minimum value of the acoustic excitation boundary in this embodiment Obtained through subjective evaluation by the human ear.

[0037] Specifically, first install a test bench that simulates the effect of the transmission shaft on the vibration, noise and fatigue of the transmission, and set the unbalance of the transmission shaft 7. and the equivalent angle , unbalance Adjustment is performed by installing balancing weights 8 of different masses.

[0038] in, , is the maximum number of test groups for imbalance, The unbalance value of the gantry drive shaft under the balance quality level G16 is as follows: , and the maximum unbalance amount of the transmission shaft under the highest test speed is not greater than 3g after the vibration acceleration signal collected by the transmission assembly 6 is subjected to Fourier transform. The unbalance amount of the bench transmission shaft under the balance quality level G16 in the ISO 1940 standard.

[0039] Adjusting the equivalent included angle of the transmission shaft 7 through the first adjusting unit and the second adjusting unit Specifically, the transition bearing seat 10 on the synchronous moving structure bearing seat adjusting plate 11 and the load motor bearing 18 on the motor support adjusting plate 19 are synchronously moved, and the number of moving the centering hole relative to the initial position is recorded as N is the number of moving the centering hole relative to the initial position when the equivalent included angle is the maximum, and the interval of the centering holes is The distance between the rightmost end of the transmission and the leftmost end of the bearing support is recorded as .

[0040] The target equivalent included angle is less than or equal to 15°.

[0041]

[0042] The number N of moving the centering hole relative to the initial position when the equivalent included angle is the maximum needs to meet the following conditions to ensure that the maximum equivalent included angle is not greater than 15°.

[0043]

[0044] When is odd, the equivalent included angle is:

[0045] When is odd, the equivalent included angle is:

[0046] wherein, is the index of the size of the equivalent included angle of each group, is the number of moving the centering hole relative to the initial position when the equivalent included angle is the maximum, is the interval of the centering holes, is the maximum test group number of the equivalent included angle, is the distance between the rightmost end of the transmission and the leftmost end of the bearing support, and in the embodiment, the maximum test group number of the equivalent included angle is preferably odd.

[0047] The unbalance amount and the different combinations of the equivalent included angle are different combinations of exciting In the process of bench vibration and noise test under different combination excitation, the specific operation is as follows, the transmission is in the highest gear, the driving motor 1 uses the speed control mode, and the load motor 17 uses the torque control mode. The driving motor 1 outputs the rated torque of the transmission, and the input speed is from 0 rpm to the highest input speed of the whole vehicle The uniform acceleration is carried out, the acceleration slope control is 10 rpm / s, and the highest speed is reached The uniform speed is kept for 10 s. The first vibration acceleration signal , the second vibration acceleration signal , the sound signal , and the speed signal are collected in the whole experiment process The first vibration acceleration signal , the second vibration acceleration signal are subjected to Fourier transform, the curve of the amplitude of the first vibration acceleration signal at the first-order component of the transmission shaft rotation frequency corresponding to the speed is obtained , the curve of the amplitude of the first vibration acceleration signal at the second-order component of the transmission shaft rotation frequency corresponding to the speed is obtained , the curve of the amplitude of the second vibration acceleration signal at the first-order component of the transmission shaft rotation frequency corresponding to the speed is obtained , the curve of the amplitude of the second vibration acceleration signal at the second-order component of the transmission shaft rotation frequency corresponding to the speed is obtained .

[0048] The simulation dynamics model is established, based on the above steps, the transmission shaft speed signal of the simulation model is obtained , the simulated first vibration acceleration signal and the simulated second vibration acceleration signal of the transmission assembly 6 in the simulation model and the experimental sensor are obtained. The simulated first vibration acceleration signal and the simulated second vibration acceleration signal are subjected to Fourier transform, the curve of the amplitude of the simulated first vibration acceleration signal at the first-order component of the transmission shaft rotation frequency corresponding to the speed is obtained , the curve of the amplitude of the simulated first vibration acceleration signal at the second-order component of the transmission shaft rotation frequency corresponding to the speed is obtained , the curve of the amplitude of the simulated second vibration acceleration signal at the first-order component of the transmission shaft rotation frequency corresponding to the speed is obtained , the curve of the amplitude of the simulated second vibration acceleration signal at the second-order component of the transmission shaft rotation frequency corresponding to the speed is obtained .

[0049] will be with , with , with , with The simulation dynamics model is iteratively optimized until the error is controlled within 10%.

[0050] Based on the adjusted simulation dynamics model, the vibration fatigue life of the transmission assembly 6 under different combined excitations is calculated get a three-dimensional data set, combined with the design fatigue life of the transmission , obtain the fatigue excitation boundary under the target fatigue life .

[0051] The sound signals under different combined excitations , respectively, 5s of uniform noise signals are intercepted, and a noise data set is obtained by combination Subjective evaluation, the number of subjective evaluation team is not less than 50, the age requirement is between 20-50 years old, the male to female ratio is 7:3, and the acoustic excitation boundary of the tolerable knocking noise is obtained through subjective evaluation .

[0052] According to the fatigue excitation boundary and the acoustic excitation boundary , the minimum values of the unbalance and the equivalent angle are obtained, and the minimum values of the unbalance and the equivalent angle are the maximum allowable unbalance and equivalent angle of the transmission matching drive shaft.

[0053] In summary, a method for simulating the influence of the drive shaft on the vibration and noise of the transmission is provided. By controlling the unbalance and equivalent angle of the drive shaft 7, the vibration and noise of the transmission assembly 6 are tested. Combined with the results of vibration fatigue simulation and subjective evaluation, the matching requirements of the unbalance and equivalent angle of the drive shaft 7 when the transmission assembly 6 is matched are obtained, which improves the reliability and comfort of the transmission assembly.

[0054] ​​​​​​​It has to be noted that the terms "first", "second", etc. as used in the description and the claims and above-mentioned figures of the application are used to distinguish between similar objects, not necessarily describing a particular sequential or chronological order. It is to be understood that the use of data "first", "second", etc., to distinguish between objects in the description and the claims is not anything more than notational and is merely intended to distinguish between two similar objects. It is further understood that data used in such a way can be interchangeable under appropriate circumstances, and embodiments of the present application described herein are capable of operation in other sequences than those explicitly described or illustrated herein. Furthermore, the terms "comprise" and "include" and variations thereof as used in the description and the claims and above-mentioned figures of the application are intended to cover both the respective case and the alternative case, i.e. to cover both the case of "comprising" and the case of "consisting of".

Claims

1. A test bench for simulating the effects of a transmission shaft on transmission vibration, noise, and fatigue, characterized by: The invention comprises a base plate (20), wherein a driving motor support (4), a bearing seat adjustment plate (11) and a motor support adjustment plate (19) are fixedly connected to the base plate (20), wherein the driving motor support (4) is fixedly connected to the upper end thereof, wherein a driving motor (1) is fixedly connected to the upper end thereof, wherein a first adjustment unit that moves forward and backward is provided on the bearing seat adjustment plate (11), wherein a second adjustment unit that moves forward and backward is provided on the motor support adjustment plate (19), wherein the first adjustment unit and the bearing seat adjustment plate (11) and the second adjustment unit and the motor support adjustment plate (19) are fixedly connected via a connecting member, wherein the driving motor (1) is rotationally connected to the first adjustment unit via a transmission shaft (7), wherein the first adjustment unit is rotationally connected to the second adjustment unit via a transition shaft (12), and wherein a balancing weight (8) is provided at one end of the transmission shaft (7) close to the first adjustment unit and is sleeved on the transmission shaft (7).

2. The test bench for simulating the influence of the transmission shaft on the vibration, noise and fatigue of the transmission according to claim 1, characterized in that: The output end of the drive motor (1) is provided with a first flexible coupling (3), one end of the first flexible coupling (3) passes through the drive motor bearing seat (2) and is rotationally connected to the output shaft of the drive motor (1), and the other end passes through the transmission support (5) and is rotationally connected to the transmission assembly (6), and the transmission assembly (6) is rotationally connected to the transmission shaft (7).

3. The test bench for simulating the influence of the transmission shaft on the vibration, noise and fatigue of the transmission according to claim 2, characterized in that: The upper end of the bearing seat adjustment plate (11) is provided with side-by-side grooves, and the first adjustment unit includes a transition bearing seat (10) installed on the upper end of the bearing seat adjustment plate (11) and a speed measuring gear plate (9) installed on the transition shaft (12), and a connecting member passes through the transition bearing seat (10) from top to bottom to fix the transition bearing seat (10) and the bearing seat adjustment plate (11).

4. The test bench for simulating the influence of the transmission shaft on the vibration, noise and fatigue of the transmission according to claim 3, characterized in that: The second adjustment unit comprises a load motor support (18), a load motor (17), and a load motor bearing seat (16) mounted on the upper end of the motor support adjustment plate (19); a transition shaft (12), an inertia disk (13), and a mounting shaft (14) are sequentially arranged on the side of the transition bearing seat (10) away from the transmission shaft (7); one end of the second flexible coupling (15) is sleeved on the mounting shaft (14), and the other end passes through the load motor bearing seat (16) and is connected to the output shaft of the load motor (17).

5. The test bench for simulating the influence of the transmission shaft on the vibration, noise and fatigue of the transmission according to claim 4, characterized in that: A vibration acceleration sensor (22) is provided on the outer shell of the transmission assembly (6). The vibration acceleration sensor (22) is connected to a signal conditioner (24) and is used to measure the vibration of the transmission assembly (6). The signal conditioner (24) is also connected to an acoustic sensor (21) and a rotation speed sensor (23). The acoustic sensor (21) is used to measure the noise of the transmission assembly (6). The rotation speed sensor (23) obtains the transmission shaft rotation speed through a speed measuring gear disc (9).

6. The test bench for simulating the influence of the transmission shaft on transmission vibration, noise and fatigue according to claim 1, characterized in that: The inertia disc (13) is used to simulate the inertia of the entire vehicle. The inertia disc (13) is provided with a plurality of dynamic balancing holes in the circumferential direction. The dynamic balancing holes are evenly distributed in the circumferential direction, and the central angle between two adjacent holes is 15°.

7. A method for simulating the influence of a transmission shaft on transmission vibration, noise and fatigue, based on the test bench for simulating the influence of a transmission shaft on transmission vibration, noise and fatigue according to any one of claims 1 to 6, characterized in that: The following steps are involved: Adjust the unbalance of the drive shaft (7) by installing balancing weights (8) of different masses , the equivalent angle of the transmission shaft (7) is adjusted by the first adjustment unit and the second adjustment unit ; For unbalance and the equivalent angle Get different combinations of incentives ; Establish a dynamic simulation model and obtain the target fatigue life based on simulation and experimental results Fatigue excitation boundary under ; Based on different incentives The sound signal , get the acoustic excitation boundary ; According to the fatigue excitation boundary Harmonic excitation boundary Obtaining the imbalance and the equivalent angle The minimum value of .

8. The method for simulating the influence of the transmission shaft on transmission vibration, noise and fatigue according to claim 7, characterized in that: The imbalance for: in, , is the maximum number of test groups for imbalance, The imbalance of the gantry drive shaft under the balance quality level G16.

9. The method for simulating the influence of the transmission shaft on transmission vibration, noise and fatigue according to claim 7, characterized in that: The equivalent angle for: in, is the index of the size of the equivalent angle of each group, is the number of centering holes moved relative to the initial position at the maximum equivalent angle, is the centering hole spacing, is the maximum number of test groups of equivalent angle and is an odd number. It is the distance between the rightmost end of the transmission and the leftmost end of the bearing support.

10. The method for simulating the influence of the transmission shaft on the vibration, noise and fatigue of the transmission according to claim 9, characterized in that: The number of centering holes moved relative to the initial position at the maximum equivalent angle : in, Round down, is the centering hole spacing.

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