Rotor bracket torsional vibration suppression design method and system based on modal strain energy and rotor bracket

Abstract

The invention provides a modal strain energy-based rotor bracket torsional vibration suppression design method and system and a rotor bracket. The method comprises the following steps of S1, collecting actual operation data of a rotor of a range extender generator; s2, carrying out vibration noise simulation analysis on the rotor to determine the significant peak frequency of the vibration response of the rotor; s3, carrying out modal contribution analysis on the rotor to determine a modal shape with significant contribution; s4, the modal strain energy and the swing modal frequency of the position, needing to be optimized, of the rotor are calculated; s5, determining a plurality of related variables, wherein the plurality of related variables form an optimization target set; and S6, calculating numerical values of all related variables meeting the target function in the optimization target set so as to find the optimal structural parameters of the rotor support of the rotor. According to the scheme, the structure of the rotor bracket of the range extender generator can be optimized, the rotor bracket obtained through optimization is proved to be effective in torsional vibration suppression, and the torsional vibration knocking level can be effectively improved.

Description

Technical Field

[0001] The present invention relates to the technical field of rotor bracket optimization design, and in particular to a rotor bracket torsional vibration suppression design method and system based on modal strain energy, and the rotor bracket. Background Art

[0002] Generators, as a power device that stores electrical energy in batteries, are widely used in plug-in and range-extended hybrid vehicles. They convert the engine's mechanical energy into electrical energy and store it in batteries, effectively solving the power source of the main drive motor. Generators have a similar structure to conventional drive motors, with key components such as stators, rotors, end covers, and bearings. When using a generator, considering the range extender scenario, the torque fluctuations from the engine due to excitation such as combustion are transmitted to the entire shaft system through the generator rotor shaft directly connected to the crankshaft. The torsional mode of the shaft system is relatively low due to the torsional stiffness of the crankshaft. The rotor structure at the end, as a cantilever feature, will cause risks such as friction and knocking in the entire air gap and near the bearings of the rotating shaft.

[0003] Patent number CN221305679U discloses a range extender, including an engine crankshaft, a rotor assembly, and fasteners. The rotor assembly includes a rotor bracket and a rotor core, and the rotor core is fixed to the side wall of the rotor bracket; the rotor bracket includes a shaft body and an outer ring body, and the rotor core is fixed to the side wall of the outer ring body.

[0004] In the above patent solution, the outer ring body can be divided into spokes and mounting sleeves, which are respectively used to connect to the shaft and to install the rotor core. In fact, the connection position of the spokes and the mounting sleeve will affect the NVH characteristics of the range extender. There is no analysis and research in the prior art on the influence of the connection position of the spokes and the mounting sleeve of the rotor bracket on the NVH characteristics of the range extender. Summary of the Invention

[0005] Based on the above-mentioned problems existing in the prior art, the present invention aims to solve the problem that the connection position of the spokes of the rotor bracket and the mounting sleeve will affect the NVH characteristics of the range extender. However, there is no technical problem in the prior art to analyze and study the influence of the connection position of the spokes of the rotor bracket and the mounting sleeve on the NVH characteristics of the range extender.

[0006] The present invention provides a method for designing a rotor support to suppress torsional vibration based on modal strain energy, which comprises the following steps: S1: Collecting actual operating data of the range extender generator rotor; S2: performing vibration noise simulation analysis on the rotor based on the collected actual operation data of the rotor to determine a significant peak frequency of the rotor vibration response; S3: Based on the significant peak frequencies determined in step S2, a modal contribution analysis is performed on the rotor to determine a modal vibration shape with a significant contribution as a key modal vibration shape; S4: determining a position on the rotor that needs to be optimized based on the determined key modal vibration shape, and calculating the modal strain energy and the oscillation modal frequency at the position that needs to be optimized; S5: determining a plurality of related variables based on the calculated modal strain energy and the swing modal frequency, wherein the plurality of related variables constitute an optimization target set; S6: Setting an objective function, calculating the values ​​of all relevant variables in the optimization target set that satisfy the objective function, thereby finding the optimal structural parameters of the rotor support of the rotor.

[0007] In some embodiments, in step S2, the method used to perform vibration noise simulation analysis on the rotor is a finite element method.

[0008] In some embodiments, in step S3 , the modal vibration modes that contribute significantly include the torsional mode of the shaft system and the oscillating mode of the rotor support.

[0009] In some embodiments, the rotor includes a shaft, a mounting sleeve, and spokes, wherein the mounting sleeve is concentrically arranged with the shaft, one end of the spoke is fixedly connected to the shaft, and the other end of the spoke is fixedly connected to the mounting sleeve; The multiple related variables in step S5 include: rotor weight, rotor inertia, spoke angle and spoke thickness.

[0010] In some embodiments, the objective function in step S6 includes a modal strain energy target value and a swing modal frequency target value.

[0011] In some embodiments, when calculating the values ​​of all relevant variables in the optimization target set that satisfy the objective function in step S6, the method used is polynomial optimization.

[0012] The present invention also provides a rotor support torsional vibration suppression design system based on modal strain energy, which is used to implement the rotor support torsional vibration suppression design method based on modal strain energy, and includes: A collection module for collecting actual operating data of the rotor of the range extender generator; a simulation analysis module, which is in communication with the acquisition module and is used to perform vibration and noise simulation analysis on the rotor based on the acquired actual operation data of the rotor, so as to determine a significant peak frequency and peak level of the rotor vibration response; a contribution analysis module, which is in communication with the simulation analysis module and is used to perform a modal contribution analysis on the rotor based on the determined significant peak frequency to determine a modal vibration shape with a significant contribution as a key modal vibration shape; a modal analysis calculation module, which is in communication with the contribution analysis module and is used to determine the position on the rotor that needs to be optimized based on the determined key modal vibration shape, and calculate the modal strain energy and swing modal frequency at the position that needs to be optimized; a variable calculation module, which is in communication with the modal analysis calculation module and is used to determine a plurality of related variables based on the calculated modal strain energy and oscillation modal frequency, wherein the plurality of related variables constitute an optimization target set; A calculation module is communicatively connected with the variable calculation module and is used to calculate the values ​​of a plurality of related variables in the optimization target set that satisfy the objective function, thereby finding the optimal structural parameters of the rotor support.

[0013] The present invention also provides a rotor bracket, which is arranged in a generator with a range extender. The rotor bracket includes a shaft, a mounting sleeve and a spoke. The mounting sleeve is arranged concentrically with the shaft, one end of the spoke is fixedly connected to the end of the shaft close to the crankshaft of the range extender engine, and the other end of the spoke is fixedly connected to the mounting sleeve; the rotor bracket is designed according to the rotor bracket torsional vibration suppression design method based on modal strain energy, and the end of the spoke away from the shaft is fixedly connected to the 1 / 2 width position of the mounting sleeve.

[0014] The beneficial effects of the present invention are: The present invention provides a rotor bracket torsional vibration suppression design method and system based on modal strain energy, which can optimize the rotor structure of the range extender generator. The optimized rotor bracket has been proven to be effective in suppressing torsional vibration and can effectively improve the torsional vibration knocking level. BRIEF DESCRIPTION OF THE DRAWINGS

[0015] In order to more clearly illustrate the technical solutions in the embodiments or the prior art, the following briefly introduces the drawings required for use in the embodiments or the description of the prior art. Obviously, the drawings described below are only some embodiments of the invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying any creative work.

[0016] Figure 1 This is a flow chart of a method for designing a rotor support to suppress torsional vibration based on modal strain energy provided by an embodiment of the present invention; Figure 2 is a schematic structural diagram of a range extender in an embodiment of the present invention; Figure 3 is a schematic structural diagram of a rotor in an embodiment of the present invention; Figure 4 is a flow chart of a method for designing a rotor support to suppress torsional vibration based on modal strain energy in an embodiment of the present invention; Figure 53. This is a modal comparison diagram before and after the rotor bracket is optimized in an embodiment of the present invention; Figure 6 is a comparison diagram of modal strain energy before and after optimization of the rotor bracket in an embodiment of the present invention; Figure 7 It is a displacement response curve diagram of the U-shaped rotor bracket at the bearing position corresponding to the crankshaft unit load in the prior art; Figure 8 3 is a displacement response curve diagram of the rotor support at the bearing position corresponding to the crankshaft unit load in an embodiment of the present invention. DETAILED DESCRIPTION

[0017] The following descriptions of the embodiments refer to the accompanying drawings to illustrate specific embodiments in which the present invention may be implemented.

[0018] The present invention provides a rotor support torsional vibration suppression design system based on modal strain energy, the structure of which is as follows: Figure 1 As shown, the rotor bracket torsional vibration suppression design system based on modal strain energy includes an acquisition module 101, a simulation analysis module 102, a contribution analysis module 103, a modal analysis calculation module 104, a variable calculation module 105 and a calculation module 106, which establish communication connections in sequence, wherein the acquisition module 101 is used to collect actual operating data of the rotor 1 of the range extender generator; The structure of the range extender is as follows Figure 2 As shown, it includes a generator and an engine, and the structure of the generator is as follows Figure 3 As shown, it includes a rotor 1 and a bearing 2, the rotor 1 includes a rotor support 11 and a rotor core 12, wherein the rotor support 11 includes a shaft 111, a mounting sleeve 112 and a spoke 113, one end of the shaft 111 is fixedly connected to the crankshaft 10 of the engine, and the other end is rotatably supported on the generator housing through the bearing 2, the mounting sleeve 112 is concentrically arranged with the shaft 111, one end of the spoke 113 is fixedly connected to one end of the shaft 111 close to the crankshaft 10, and the other end is fixedly connected to 1 / 2 width position of the mounting sleeve 112; the rotor core 12 is fixedly arranged on the outer wall of the mounting sleeve 112 and is located at 1 / 2 width position of the mounting sleeve 112.

[0019] The simulation analysis module 102 is in communication with the acquisition module 101, and is used to perform vibration noise simulation analysis on the rotor 1 based on the actual operation data of the rotor 1 acquired, so as to determine the significant peak frequency and peak level of the vibration response of the rotor 1; the contribution analysis module 103 is in communication with the simulation analysis module 102, and is used to perform modal contribution analysis on the rotor 1 based on the determined significant peak frequency, so as to determine the modal vibration shape with significant contribution as the key modal vibration shape; the modal analysis calculation module 104 is in communication with the contribution analysis module 103, and is used to perform modal contribution analysis on the rotor 1 based on the determined significant peak frequency, so as to determine the modal vibration shape with significant contribution as the key modal vibration shape. According to the determined key modal vibration mode, the position on the rotor 1 that needs to be optimized is determined, and the modal strain energy and swing modal frequency at the position that needs to be optimized are calculated; the variable calculation module 105 is communicated with the modal analysis calculation module 104 to determine multiple related variables based on the calculated modal strain energy and swing modal frequency, and the multiple related variables constitute an optimization target set; the calculation module 106 is communicated with the variable calculation module 105 to calculate the values ​​of multiple related variables in the optimization target set that meet the objective function, so as to find the optimal structural parameters of the rotor bracket 11.

[0020] The present invention also provides a method for designing a rotor support to suppress torsional vibration based on modal strain energy, which is implemented based on the above-mentioned rotor support torsional vibration suppression design system based on modal strain energy, such as Figure 4 The flowchart of the method for designing a rotor support to suppress torsional vibration based on modal strain energy is shown, which includes the following steps: S1: Collecting actual operating data of the range extender generator rotor; In an actual range extender generator operating environment, vibration sensors (such as acceleration sensors) and noise sensors are installed to collect vibration and noise data of the rotor.

[0021] S2: Based on the collected actual operating data of the rotor, a vibration noise simulation analysis is performed on the rotor using a finite element method to determine a significant peak frequency and peak level of the rotor vibration response; When using the finite element method to simulate rotor vibration and noise, a virtual model of the rotor is first created using the finite element method. Parameters such as the rotor's geometry, dimensions, material, and actual operating data must be accurately input into the finite element analysis software. The software's calculation function simulates the rotor's vibration response under different operating conditions, generating a vibration spectrum curve and preliminarily determining the frequency locations of potential significant peaks and the corresponding vibration amplitudes.

[0022] S3: Based on the significant peak frequencies determined in step S2, a modal contribution analysis is performed on the rotor to determine a modal vibration shape with a significant contribution as a key modal vibration shape; Modal analysis is an important method for studying the dynamic characteristics of structures. It decomposes complex vibration phenomena into a series of simple harmonic vibrations, each corresponding to a modal shape and natural frequency. For the rotor described above, its vibration response under different excitations is the result of the combined action of numerous modes.

[0023] Among the many modes, each contributes differently to a specific response (such as vibration and noise). Modal contribution analysis is used to quantify the contribution of each mode to the response of interest. This calculation can determine which modes are the key factors causing problems such as vibration and noise. After determining the significant peak frequency, modal contribution analysis is performed using relevant algorithms (such as the Craig-Bampton method) to calculate the contribution of each mode to the vibration response at the significant peak frequency. Based on the modal contribution calculation results, the modal shapes with the largest contribution are selected, namely the modal shapes with significant contribution. These key modal shapes are the root cause of the rotor's large vibration response at the significant peak frequency. Identifying them helps to gain a deeper understanding of the rotor's vibration and noise characteristics, providing key information for subsequent optimization design.

[0024] Specifically, the key modal vibration modes correspond to the torsional mode of the shaft system and the swing mode of the rotor bracket, respectively. Among them, the torsional mode of the shaft system is transmitted to the motor side. Due to its heavy weight, it is expressed in the form of the swing mode of the rotor bracket. Therefore, it is necessary to improve the level of the swing mode to improve the knocking. Therefore, the swing mode of the rotor bracket is used as an optimization item in the subsequent process.

[0025] S4: determining a position on the rotor that needs to be optimized based on the determined key modal vibration shape, and calculating the modal strain energy and the oscillation modal frequency at the position that needs to be optimized; Based on the identified key mode shapes, we can visually identify which areas of the rotor experience larger displacements and which areas experience smaller displacements during vibration. Areas with larger displacements are often where vibration energy is concentrated and stress is high, representing key locations that lead to significant peaks in the vibration response. Therefore, these locations are the rotor locations that require optimization. Optimizing these locations can more effectively alter the rotor's vibration characteristics and reduce the vibration response.

[0026] Strain energy refers to the potential energy stored within an object during its deformation. Modal strain energy is calculated using vibration modes and stiffness. Modal strain energy shows the location where energy absorption is most concentrated under each modal vibration mode. The element strain energy (MSE) of the i-th mode is defined as follows: In this formula, represents the i-th order mode shape, that is, the modal displacement vector, represents the element stiffness matrix.

[0027] The higher the modal strain energy, the greater the local displacement, and the lower the stiffness of the structure. When subjected to an excitation consistent with the vibration mode, the high strain energy position is more likely to deform. Specifically, in this embodiment, the position to be optimized in step S4 includes the rotor bracket. The modal displacement value and stiffness that form the modal strain energy are optimized by adjusting the thickness, spoke shape, angle and other parameters of the rotor bracket of the rotor to reduce the modal strain energy; the modal calculation formula is: In this formula, f represents the modal frequency, k represents the effective stiffness, and m represents the effective weight.

[0028] Modal contribution analysis: By calculating the frequency response, we can analyze which mode contributes the most and whether it is a positive contribution or a negative contribution. The positive contribution needs to be optimized by suppressing the mode and optimizing the peak frequency of interest.

[0029] Modal strain energy reflects the deformation and energy distribution of various rotor components under different modes. Calculating modal strain energy can determine the strain energy distribution at various locations on the rotor under different modes, thereby identifying key areas with high strain energy. The swing modal frequency reflects the rotor's dynamic characteristics under swing vibration. Calculating the swing modal frequency can reveal the rotor's stiffness and mass distribution along the swing direction.

[0030] For a direct-connected engine-generator structure, the torsional excitation of the engine is usually lower than 2000Hz. To ensure that the structural mode and the excitation frequency are effectively avoided, the design modal frequency is required to be no lower than 2500Hz. Based on previous practical experience: the modal strain energy MSE is required to be no lower than 1000Hz (near the 600Hz frequency point), the weight m does not exceed 10.5kg, and the inertia J is between 0.06 and 0.08kg / m. 2 , where the lower limit ensures sufficient damping to suppress torsional excitation, and the upper limit is to ensure that the response speed is not too slow, where the moment of inertia ; S5: determining a plurality of related variables based on the calculated modal strain energy and the swing modal frequency, wherein the plurality of related variables constitute an optimization target set; Based on modal strain energy and oscillation modal frequency, multiple related variables are calculated, including rotor weight, rotor inertia, spoke angle, and spoke thickness. These related variables are interrelated and influence each other. For example, changing the spoke angle or spoke thickness directly affects the rotor's mass and stiffness distribution, thereby changing the rotor's inertia and modal strain energy distribution. Changes in rotor weight and inertia, in turn, affect the oscillation modal frequency. These multiple related variables are combined to form a target set. This target set represents the parameter ranges or target values ​​that require focus and adjustment during the optimization of rotor vibration and noise performance. This target set is related to the rotor's vibration and noise performance, such as modal strain energy below a certain value and oscillation modal frequency within a specific range. It also includes some geometric and physical parameters of the rotor support, such as rotor weight, rotor inertia, spoke angle, spoke thickness, and strain energy level, and other desired target values ​​or allowable variation ranges. This target set provides a clear direction and goal for subsequent optimization design.

[0031] Based on the preliminary target values: oscillation modal frequency Fre, modal strain energy MSE upper limit, weight m upper limit, and appropriate range of moment of inertia J, optimize the rotor structural parameters, mainly including the spoke angle θ of the rotor bracket, spoke thickness T, and the distance L1 from the spoke center to the bearing side end of the mounting sleeve; It can be expressed as a multi-variable multi-objective function relationship: In the above formula, MSE is the modal strain energy; Fre is the oscillation modal frequency; m is the rotor mass; J is the rotor inertia; θ is the spoke span angle; T is the spoke thickness; L1 is the distance from the spoke center to the bearing end of the mounting sleeve; S6: Setting an objective function and performing polynomial optimization to calculate the values ​​of all relevant variables in the optimization objective set that satisfy the objective function, thereby finding the optimal structural parameters of the rotor support of the rotor. Specifically, the objective function includes a target value for modal strain energy and a target value for oscillation modal frequency.

[0032] Using optimization algorithms (such as genetic algorithms and particle swarm optimization), extensive calculations and evaluations are performed within the defined optimization objective set to find the optimal multivariable combination that satisfies both the modal strain energy and the swing modal frequency. These algorithms automatically adjust the values ​​of each variable based on the objective function (related indicators of modal strain energy and swing modal frequency) to ultimately find the optimal solution.

[0033] Based on multivariable target optimization, it is analyzed whether the target values ​​of the swing modal frequency and modal strain energy are met. If so, the optimization is completed; if not, the structural parameters are optimized until the above goals are met.

[0034] According to the modal test model, the modal frequency and vibration shape characteristics of the current problem point are identified, that is, the frequency is The rotor's oscillatory mode at , and focus on multiple frequency points: 、 、 The strain energy performance.

[0035] Based on the strain energy level, the structural parameters of the rotor bracket are optimized, including the size of L1, the weight m of the rotor, the inertia J, and the frequency index of the target vibration mode. The target values ​​of each structural parameter are: ;weight Inertia ,frequency ; In order to further clarify the strain energy level, three modal frequency points are selected: 、 、 , compare the strain energy levels before and after optimization; In combination with the above objectives, the above indicators are optimized by optimizing the spoke angle θ, spoke thickness T, and the distance L1 between the spoke center and the rear bearing rotor end of the rotor bracket; Combined with the target optimization, the spoke angle is 24 degrees, the spoke thickness T is 5 mm, L1 is 0.5 L, and m is 9.5 kg. , f is 2654Hz.

[0036] Furthermore, after finding a combination of related variables that meets these dual objectives, the rotor structure corresponding to these parameters needs to be simulated and verified through methods such as finite element analysis. This involves checking whether the rotor's vibration response, modal characteristics, and other aspects meet the design requirements under the new structural parameters, while also evaluating their impact on the overall performance of the range extender generator. Finally, the optimal values ​​of the multiple related variables that have been verified are determined as the final rotor structural parameters, which will be used to guide rotor design and manufacturing. In actual applications, further fine-tuning and optimization can be carried out based on test feedback to continuously improve rotor performance and ensure good vibration and noise performance in actual operation.

[0037] The embodiment provides a rotor bracket torsional vibration suppression design method based on modal strain energy, and finally optimizes the design of the U-shaped rotor bracket in the prior art to Figure 3 One of the optimization contents of the T-shaped rotor bracket shown is: optimizing the end of the spoke 113 away from the shaft 111 from the leftmost end of the mounting sleeve 112 to the 1 / 2 width position of the mounting sleeve 112.

[0038] Comparative Verification Figure 5The following are the modal comparison diagrams of the rotor bracket before and after optimization. The left diagram shows the U-shaped rotor bracket, and the right diagram shows the T-shaped rotor bracket. This shows that the modal of the optimized rotor bracket is significantly improved, effectively avoiding the excitation of the low-frequency band of the engine. Figure 6 The figure shows the comparison of the modal strain energy of the rotor bracket before and after optimization. The left figure is a U-shaped rotor bracket, and the right figure is a T-shaped rotor bracket, indicating that the modal strain energy is significantly reduced after optimization. Figure 7 is the displacement response curve of the U-shaped rotor bracket at the bearing position corresponding to the unit load of the crankshaft, Figure 8 This is the displacement response curve of the T-type rotor bracket at the bearing position corresponding to the unit load of the crankshaft. It can be seen that the response of the T-type rotor bracket is lower at the same frequency, that is, under the same excitation, the torsional vibration performance of the T-type rotor bracket is better.

[0039] Table 1 shows the comparison of the z-direction response amplitude of the bearing end under unit force between the U-shaped rotor bracket and the T-shaped rotor bracket. Table 2 shows the measured optimization of the T-shaped rotor bracket compared to the conventional solution (U-shaped rotor bracket): Table 1 Comparison of the z-direction response amplitude of the bearing end under unit force between the U-shaped rotor bracket and the T-shaped rotor bracket In Table 1, B0 represents the U-shaped rotor bracket in the prior art, and B2 represents the rotor bracket optimized using the method of this embodiment (i.e., the T-shaped rotor bracket). As can be seen from Table 1, compared with the U-shaped rotor bracket, the Z-direction response of the T-shaped rotor bracket is significantly reduced at multiple typical frequency points, indicating that B2 is better than B0 and the structural optimization is effective.

[0040] Table 2 Measured vibration performance of the rotor bracket in this embodiment compared with the conventional solution (U-shaped rotor bracket) As can be seen from Table 2, through the measured vibration performance of the range extender, the T-type rotor bracket has significantly reduced torsional vibration at multiple different speed points along the torsional vibration direction compared with the U-type rotor bracket, and the torsional vibration is significantly improved, which proves that the T-type rotor bracket is superior to the U-type rotor bracket and the structural optimization is effective.

[0041] In summary, the modal strain energy-based rotor bracket torsional vibration suppression design method and system provided by the present invention can optimize the rotor structure of the range extender generator, and the optimized rotor bracket has been proven to be effective in suppressing torsional vibration and can effectively improve the torsional vibration knocking level.

[0042] It should be noted that although the present invention is disclosed above with specific embodiments, the above embodiments are not intended to limit the present invention. Ordinary technicians in this field can make various changes and modifications without departing from the spirit and scope of the present invention. Therefore, the scope of protection of the present invention shall be based on the scope defined by the claims.

Claims

1. A method for designing a rotor support to suppress torsional vibration based on modal strain energy, characterized in that: The following steps are involved: S1: Collecting actual operating data of the range extender generator rotor; S2: performing vibration noise simulation analysis on the rotor based on the collected actual operation data of the rotor to determine a significant peak frequency of the rotor vibration response; S3: Based on the significant peak frequencies determined in step S2, a modal contribution analysis is performed on the rotor to determine a modal vibration shape with a significant contribution as a key modal vibration shape; S4: determining a position on the rotor that needs to be optimized based on the determined key modal vibration shape, and calculating the modal strain energy and the oscillation modal frequency at the position that needs to be optimized; S5: determining a plurality of related variables based on the calculated modal strain energy and the swing modal frequency, wherein the plurality of related variables constitute an optimization target set; S6: Setting an objective function, calculating the values ​​of all relevant variables in the optimization target set that satisfy the objective function, thereby finding the optimal structural parameters of the rotor support of the rotor.

2. The method for designing a rotor support to suppress torsional vibration based on modal strain energy according to claim 1, characterized in that: In step S2, the method used for performing vibration noise simulation analysis on the rotor is the finite element method.

3. The method for designing a rotor support to suppress torsional vibration based on modal strain energy according to claim 1, characterized in that: In step S3, the modal vibration shapes that contribute significantly include the torsional mode of the shaft system and the oscillating mode of the rotor support.

4. The method for designing a rotor support to suppress torsional vibration based on modal strain energy according to claim 1, characterized in that: The rotor includes a shaft, a mounting sleeve, and spokes, wherein the mounting sleeve is concentrically arranged with the shaft, one end of the spoke is fixedly connected to the shaft, and the other end of the spoke is fixedly connected to the mounting sleeve; The multiple related variables in step S5 include: rotor weight, rotor inertia, spoke angle and spoke thickness.

5. The method for designing a rotor support to suppress torsional vibration based on modal strain energy according to claim 1, characterized in that: The objective function in step S6 includes a modal strain energy target value and a swing modal frequency target value.

6. The method for designing a rotor support to suppress torsional vibration based on modal strain energy according to claim 1, characterized in that: In step S6, when calculating the values ​​of all relevant variables in the optimization target set that satisfy the objective function, the method used is polynomial optimization.

7. A rotor support torsional vibration suppression design system based on modal strain energy, used to implement the rotor support torsional vibration suppression design method based on modal strain energy according to any one of claims 1 to 6, characterized in that: include: A collection module for collecting actual operating data of the rotor of the range extender generator; a simulation analysis module, which is in communication with the acquisition module and is used to perform vibration and noise simulation analysis on the rotor based on the acquired actual operation data of the rotor, so as to determine a significant peak frequency and peak level of the rotor vibration response; a contribution analysis module, which is in communication with the simulation analysis module and is used to perform a modal contribution analysis on the rotor based on the determined significant peak frequency to determine a modal vibration shape with a significant contribution as a key modal vibration shape; a modal analysis calculation module, which is in communication with the contribution analysis module and is used to determine the position on the rotor that needs to be optimized based on the determined key modal vibration shape, and calculate the modal strain energy and swing modal frequency at the position that needs to be optimized; a variable calculation module, which is in communication with the modal analysis calculation module and is used to determine a plurality of related variables based on the calculated modal strain energy and oscillation modal frequency, wherein the plurality of related variables constitute an optimization target set; A calculation module is communicatively connected with the variable calculation module and is used to calculate the values ​​of a plurality of related variables in the optimization target set that satisfy the objective function, thereby finding the optimal structural parameters of the rotor support.

8. A rotor bracket, provided in a generator with a range extender, comprising a shaft, a mounting sleeve, and spokes, wherein the mounting sleeve is concentrically arranged with the shaft, one end of the spoke is fixedly connected to an end of the shaft close to the crankshaft of the range extender engine, and the other end of the spoke is fixedly connected to the mounting sleeve; characterized in that: The rotor bracket is designed according to the rotor bracket torsional vibration suppression design method based on modal strain energy as described in claims 1 to 6, and the end of the spoke away from the shaft is fixedly connected to the 1 / 2 width position of the mounting sleeve.

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