Electrically-assisted turbocharger rotor experiment table and application

Abstract

The invention discloses an electrically-assisted turbocharger rotor experiment table and application thereof, which is characterized in that an axial locking nut, a thrust bearing and a floating ring bearing are used for supporting a shafting structure, equivalent compressor blades and a turbine disc are used for simulating mass, and a middle motor structure is used for driving; according to the invention, the static contact parameter identification experiment and the dynamic characteristic and parameter matching relation experiment of the electrically-assisted turbocharger can be realized. According to the method, the axial locking device is used for fixing the shafting part, adjusting the tightening torque and the tightening step length to change the pre-tightening parameters, and the static contact parameters are identified by combining metal processing process parameters. The matching form and matching parameters of the middle motor and the rotating shaft are changed, so that a dynamic characteristic and parameter matching relation experiment can be realized; an equivalent simulation counterweight disc is arranged on the central rotating shaft, and the weight and the number of counterweight bolts are adjusted to simulate rotor unbalance and typical assembly fault experiments.

Description

Technical Field

[0001] The invention relates to the technical field of turbocharger test benches, and in particular to a novel electrically assisted turbocharger rotor test bench and application thereof taking into account a connection structure and an assembly process. Background Art

[0002] With the development of the automobile industry and internal combustion engines, exhaust gas turbocharging technology has been widely used in engine design due to its advantages in fuel economy, environmental protection of exhaust gas emissions and engine performance improvement. However, due to the influence of changing load environment, harsh working environment and significant hysteresis effect, the turbocharger rotor system is prone to fatigue failure, overspeed damage and other faults. In order to solve the engineering problems existing in traditional turbochargers, the design of high-speed motor-assisted turbochargers came into being. The design of new electric-assisted turbochargers needs to consider more complex shaft assembly structures and assembly process errors, which will lead to prominent overall vibration problems and vibration damage of some components. The introduction and assembly of the motor will change the initial structure of the rotor system, so that there is uncertainty in the structural vibration response; and with the prominence of the vibration problem, the contact state between the shaft system mating parts will also change during processing and assembly. This contact nonlinearity will have a greater impact on the vibration characteristics of the rotor system, and the parameter uncertainty caused by the connection structure will also bring challenges to the structural dynamics design of the turbocharger. The overall vibration characteristics are highly dependent on the changes in the axial preload assembly parameters, the influence of the shaft system component assembly process and the stability.

[0003] However, the experimental platform in the prior art has the following problems:

[0004] 1. The test bench in the prior art usually greatly simplifies the shaft system components, and the matching form and matching parameters of the sleeve and the rotating shaft, the motor and the rotating shaft are ignored, or the shaft system components are simply equivalent in mass and moment of inertia, and then integrated into the central rotating shaft.

[0005] 2. Since the traditional test bench adopts an integrated design method as a whole and there is no precise test bench processing method, the contact effect between the axial components is completely ignored. The existing test bench cannot carry out experimental research and testing on the contact characteristics of the rotor test bench under different working conditions.

[0006] 3. In the electric-assisted supercharger test bench, the driving method is usually that an external motor is connected to the central shaft through a coupling, and the shaft design at the original high-speed motor is simplified to an equivalent disc. This structure ignores the influence of the coupling between the motor and the rotor system, and the influence of the assembly problem between the motor and the rotor system on the performance of the system is also ignored.

[0007] 4. Preload has a significant impact on the performance of the system. Preload and assembly clearance are affected by factors such as the step length and number of steps in the bolt tightening process, as well as the rotation speed of the shaft. Under different operating conditions such as static, low speed or high speed, it presents a complex evolution trend. In particular, under conditions such as high-speed rotation of the shaft causing excessive vibration, it is necessary to analyze the relationship between parameters such as bolt preload, tightening steps, tightening step length, axial structural clearance and rotor amplitude deviation. However, the existing test bench cannot meet the above requirements. Summary of the invention

[0008] The purpose of the present invention is to overcome the deficiencies in the prior art and solve the problem that the test bench in the prior art is difficult to consider the changes in component contact effects and the influence of assembly process factors under high speed or working speed margin, and to provide an electrically assisted turbocharger rotor test bench and application, which are mainly used for static contact parameter identification and dynamic characteristic experiments of complex combined rotor shaft structure under simulation of typical rotor failures and assembly problems.

[0009] The test bench integrates the existing finishing technology, decomposes the integrated processing process of the traditional rotor test bench into different shaft system components, considers the contact form and contact parameters between different shaft system components, and controls the initial static displacement of the rotor test bench, so as to effectively identify the static parameters of the rotor structure considering the contact effect. At the same time, the bearing seat is processed in a split manner to realize the introduction of the mid-mounted motor of the electric-assisted turbocharger. Considering the influence of the assembly form of the split bearing and the mid-mounted motor, the dynamic characteristics of the rotor system are effectively measured. The physical parameters of the compressor impeller and the turbine disk are equivalent to simplify the complex curved blade shape. At the same time, the additional counterweight bolts on the counterweight plate can also be repeatedly disassembled and assembled to simulate the unbalanced faults of the impeller and the rotor. Taking into account the influence of the connection contact effect and the assembly process, the new structural design of the traditional electric-assisted turbocharger rotor test bench realizes the design of a new rotor test bench with multi-factor and multi-function coupling.

[0010] The objective of the present invention is achieved through the following technical solutions:

[0011] An electrically assisted turbocharger rotor test bench is provided, which introduces the influence of axial connection structure and assembly process factors, and comprises a support, on the left and right sides of which a first bearing seat and a second bearing seat are separately fixed, a compressor wheel seat and a turbine seat are respectively fixed on the outer sides of the first bearing seat and the second bearing seat, a compressor impeller and a turbine disk are respectively installed in the compressor wheel seat and the turbine seat, and a floating ring bearing, a thrust limit bearing and an elastic sealing ring are both arranged in the first bearing seat and the second bearing seat for supporting a central rotating shaft;

[0012] Both ends of the central rotating shaft are fastened by locking nuts, and outer end covers are installed on the outer sides of the compressor wheel seat and the turbine seat. The shaft sleeve and the motor rotor are connected with clearance fit on the central rotating shaft between the first bearing seat and the second bearing seat;

[0013] The compressor wheel seat and the turbine seat are both provided with pipeline interfaces and flow guides, and oil film is filled in the floating ring bearing and the thrust limit bearing through the pipeline interfaces and the flow guides; the compressor wheel seat and the turbine seat are both provided with mounting holes for mounting eddy current sensors;

[0014] A plurality of non-contact displacement sensors are also provided on one side of the central rotating shaft between the first bearing seat and the second bearing seat for measuring the lateral vibration of the entire central rotating shaft.

[0015] Furthermore, the front of the central shaft is connected to the first bearing seat through the shaft sleeve, and the rear of the central shaft is directly connected to the second bearing seat; the concentricity and initial static displacement of the central shaft, the shaft sleeve and the motor rotor are affected by different support forms.

[0016] Furthermore, a reference groove is provided on the support, which is used to align the center lines of the compressor wheel seat and the turbine seat with the reference groove during installation to ensure structural centering.

[0017] Furthermore, by changing the tightening torque of the locking nut with a torque wrench, the magnitude of the axial preload force and the preload step length are directly changed, thereby changing the shaft connection stiffness of the central shaft.

[0018] Furthermore, elastic sealing rings are arranged between the central rotating shaft and the compressor wheel seat and the turbine seat, and two elastic sealing rings are arranged on the central rotating shaft and the turbine seat respectively.

[0019] Furthermore, the central rotating shaft is rotatably connected to the first bearing seat and the second bearing seat through a floating ring bearing; the inner end cover is installed on the opposite side of the first bearing seat and the second bearing seat through a number of fixing bolts; the pre-tightening force of the fixing bolts and the locking nuts can affect the inclination of the axis of the central rotating shaft and affect whether the central rotating shaft is protruding.

[0020] Furthermore, the compressor impeller disc and the turbine disc are used to simulate the counterweight disc, and the unbalanced state of the central rotating shaft is simulated by adjusting the weight and number of the fixing bolts.

[0021] The present invention also provides an application of an electrically assisted turbocharger rotor test bench, in which different torques are applied to the locking nut by a torque wrench to change the size of the axial preload force, and the thrust limit bearing is used to fix the axial displacement while transmitting the axial preload force to tighten the shaft system components as a whole. The compressor impeller and the turbine disk are machined with scales to obtain static contact deformation, and a structural static contact parameter identification experiment is carried out based on the relationship between the metal parts processing process parameters; the shaft system components include a shaft system sleeve and a motor rotor.

[0022] The present invention also provides an application of an electrically assisted turbocharger rotor test bench, which processes a plurality of motor rotors with different inner diameters, controls the matching parameters with the central rotating shaft through different matching forms and small clearance matching amounts, and realizes the characteristic experiment of compressor impeller and turbine disk movement at different speeds through displacement sensors and eddy current sensors.

[0023] The present invention also provides an application of an electrically assisted turbocharger rotor test bench, which constructs the unbalanced mass of the central rotating shaft by adjusting the weight and number of counterweight bolts on the counterweight plate; conducts experiments on impeller dynamic characteristics, motor rotor amplitude and axis trajectory at different speeds, and simulates classic fault and assembly problem experiments.

[0024] Compared with the prior art, the technical solution of the present invention has the following beneficial effects:

[0025] 1. High-precision matching control and vibration characteristics research: This invention controls the matching clearance of the motor shaft through precision machining technology, and can carry out experimental research on the effects of various radial matching forms and matching parameters on the vibration characteristics of the structure. Through careful consideration of the complex shaft system structure, the response accuracy and experimental efficiency of the contact effect on the dynamic characteristics of the rotor system are significantly improved.

[0026] 2. Analysis of the influence of assembly process on vibration characteristics: This invention uses the shaft end locking nut and the split-processed bearing seat, and studies the influence of these process variables on the static characteristics (such as axis alignment and shaft flexural deformation) and dynamic characteristics (such as turntable, motor vibration amplitude and axis trajectory) of the central shaft by adjusting the preload force, tightening steps and step length of the fixing bolts connected to the support. This provides an experimental basis for revealing the influence of assembly process factors on the vibration characteristics of the rotor system.

[0027] 3. Unbalanced simulation and fault test function: The counterweight plate set on the central shaft can simulate the unbalanced state of the shaft by adjusting the number and weight of the counterweight bolts. This test bench can simulate dynamic characteristics experiments such as impeller dynamic characteristics, motor amplitude, axis trajectory, etc. at different speeds, effectively reproduce and study the impact of assembly processes and typical faults on system performance, and further promote fault diagnosis and optimization design of supercharger rotor systems.

[0028] 4. Static parameter identification of contact effect: Through the independently designed shaft sleeve and floating ring bearing matching form of the test bench, the static contact parameters in the complex combined rotor shaft structure are accurately identified. The influence of variables such as contact nonlinearity and assembly clearance on static characteristics is comprehensively analyzed, which helps to optimize the structural design and process adjustment of the electric-assisted turbocharger.

[0029] 5. Multi-factor coupling research platform: The present invention successfully realizes the multifunctional integration and multi-factor coupling research of the new test bench by introducing a split bearing seat and a mid-mounted motor assembly form, as well as the equivalence of the physical parameters of the compressor impeller and the turbine disc, providing a reliable experimental platform for analyzing complex contact and assembly effects under high speed margin.

[0030] 6. Accurate measurement of dynamic characteristics experiment: The test bench of the present invention is equipped with multiple non-contact displacement sensors and eddy current sensors, which can accurately measure the lateral vibration and dynamic response of the central shaft. Combined with the assembly form and operating conditions under different working conditions, the measurement and experimental analysis capabilities of the dynamic characteristics of the supercharger rotor system are further improved. BRIEF DESCRIPTION OF THE DRAWINGS

[0031] Figure 1 It is a schematic diagram of the overall side structure of the rotor test bench of the present invention.

[0032] Figure 2 for Figure 1 Cross-sectional view along the BB direction.

[0033] Figure 3 It is an axial cross-sectional view of the sealing structure.

[0034] Figure 4 This is a schematic diagram of the structure of a single split-type bearing seat.

[0035] Figure 5 This is a front cross-sectional view of a single split-machined bearing seat.

[0036] Figure 6 This is a cross-sectional view from a top view of a single split-machined bearing seat.

[0037] Figure 7 It is a cross-sectional view of the shafting sleeve.

[0038] Figure numerals: 1, support, 2, compressor wheel seat, 3, locking nut, 4, compressor impeller, 5, elastic sealing ring, 6, thrust limit bearing, 7, floating ring bearing, 8, turbine seat, 9, turbine disk, 10, central shaft, 11, pipeline interface, 12, motor rotor, 13, shaft sleeve, 14, inner end cover, 15, first bearing seat, 16, turbine, 17, outer end cover, 18-second bearing seat DETAILED DESCRIPTION

[0039] In order to make the purpose, technical solutions and advantages of the present invention more clearly understood, the present invention is further described in detail below in conjunction with the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are only used to explain the present invention and are not intended to limit the present invention. In addition, the technical features involved in the various embodiments of the present invention described below can be combined with each other as long as they do not conflict with each other.

[0040] like Figure 1 and Figure 2 As shown, the present embodiment provides an electrically assisted turbocharger rotor test bench, which introduces the influence of the axial connection structure and the assembly process factors. The test bench includes a support 1, on which the first bearing seat 15 and the second bearing seat 18 are fixed in a split manner on the left and right sides of the support 1. The outer sides of the first bearing seat 15 and the second bearing seat 18 are respectively fixed with a compressor wheel seat 2 and a turbine seat 8. In order to avoid air turbulence, the compressor wheel seat and the turbine seat are respectively installed with a compressor impeller 4 and a turbine disk 9, and are respectively connected to the first bearing seat and the second bearing seat as a whole through fixing bolts; the split installation is used to simulate the guide volute system where the compressor impeller 4 and the turbine disk 9 are located. The first bearing seat 15 and the second bearing seat 18 are both provided with a floating ring bearing 7, a thrust limit bearing 6 and an elastic sealing ring 5 for supporting the central rotating shaft 10; the mid-mounted motor is coupled with the rotor system to simulate the electrical assistance characteristics of a high-speed motor.

[0041] Both ends of the central rotating shaft 10 are fastened by locking nuts 3, and outer end covers 17 are installed on the outer sides of the compressor wheel seat 2 and the turbine seat 8. The shaft sleeve 13 and the motor rotor 12 are connected with clearance fit on the central rotating shaft 10 between the first bearing seat 15 and the second bearing seat 18;

[0042] The compressor wheel seat 2 and the turbine seat 8 are both provided with a pipeline interface 11 and a flow guide channel, through which an oil film is filled in the floating ring bearing 7 and the thrust limit bearing 6; the compressor wheel seat 2 and the turbine seat 8 are both provided with mounting holes for installing eddy current sensors; the eddy current sensor is installed on a magnetic seat and fixed to the support through the magnetic seat, and the probe is extended into the mounting hole for non-contact measurement.

[0043] A plurality of non-contact displacement sensors are also provided on one side of the central shaft 10 between the first bearing seat 15 and the second bearing seat 18 to measure the lateral vibration of the central shaft as a whole. The displacement sensor is fixed on the support and connected to the preamplifier. The probe is close to the central shaft for non-contact measurement.

[0044] Specifically, the counterweight plate simulating the compressor impeller 4 in the compressor wheel seat 2 is axially pre-tightened by the locking nut 3 through a threaded connection locking device, and the overall axial displacement is limited by the thrust limit bearing 6 on the right side, and the axial force is transmitted to the shaft sleeve structure connected to the floating ring bearing 7. The motor rotor 12 structure is pre-stressed on the right part of the central shaft as a whole. This combined shaft structure can take into account the contact effect between components and the change of contact effect under high speed conditions and within the working speed margin range. The turbine seat 8 is also limited by the simulated turbine counterweight plate through the locking nut and thrust bearing. The pipeline interface 11 and the guide channel arranged on the left and right bearing seats can introduce lubricating oil through the oil pump under working conditions, providing a suitable working environment for the floating ring bearing.

[0045] Preferably, the front of the central rotating shaft 10 is connected to the first bearing seat 15 through the shaft sleeve 13, and the rear of the central rotating shaft 10 is directly connected to the second bearing seat 18; the concentricity and initial static displacement of the central rotating shaft 10, the shaft sleeve 13 and the motor rotor 12 are affected by different support forms.

[0046] Preferably, a reference groove is provided on the support 1, so that the center lines of the compressor wheel seat 2 and the turbine seat 8 are aligned with the reference groove during installation to ensure structural centering.

[0047] Preferably, the tightening torque of the locking nut 3 is changed by a torque wrench, thereby directly changing the size of the axial preload force and the preload step, thereby changing the shaft connection stiffness of the central shaft 10 .

[0048] Preferably, elastic sealing rings are arranged between the central rotating shaft and the compressor wheel seat and the turbine seat, and the two elastic sealing rings are respectively arranged on the central rotating shaft and the turbine seat; the central rotating shaft and the first bearing seat and the second bearing seat are rotatably connected through floating ring bearings; the inner end cover 14 is installed on the opposite side of the first bearing seat and the second bearing seat through a plurality of fixing bolts; the pre-tightening force of the fixing bolts and the locking nut 3 can affect the axial inclination of the central rotating shaft and affect whether the central rotating shaft is protruding; a counterweight plate is also arranged on the central rotating shaft 10, and a plurality of counterweight bolts are detachably connected to the counterweight plate, and the weight and number of the counterweight bolts are adjusted to simulate the unbalanced state of the central rotating shaft.

[0049] See Figure 1 , showing the axial assembly details of the compressor wheel seat and turbine seat and the radial matching details of the shaft system components. The split bearing seat is connected to the support 1 through fixing bolts, and is axially connected to the turbine seat through hexagonal bolts. The outer side of the central shaft 10 is covered with a sleeve structure with clearance fit and a motor rotor structure.

[0050] Figure 3The sealing structure is shown, which is composed of an elastic sealing ring 5 and a sealing end cover, and can provide appropriate oil pressure and oil sealing performance for the operation of the thrust limit bearing and the floating ring bearing.

[0051] Figure 4 The front view of a single split-type bearing seat is shown. The bearing seat and the bearing end cover are provided with multiple guide ports in different directions, which can be connected to the pipeline interface to provide an oil circuit environment. At the same time, after drilling, a sensor can be inserted to measure the oil film pressure, temperature and lubrication parameters.

[0052] Figure 5 The cross-sectional view of the bearing seat is shown. The guide port and drainage channel can provide space for the oil circuit, which is connected to the floating ring bearing and thrust limit bearing to provide a suitable working environment. At the same time, the external sealing structure can prevent the leakage of lubricating oil.

[0053] Figure 6 A cross-sectional view of the bearing seat from a top view is shown, showing the connection between the bearing seat and the turbine seat, which is bolted together by long bolts, and the structure of the elastic sealing ring.

[0054] Figure 7 The cross-sectional view of the entire shaft sleeve 13 is shown. The left end has a small inner recess because it needs to be connected to the floating ring bearing 7 and the inner end cover 14 on the first bearing seat 15; the right end is in tight contact with the motor rotor.

[0055] Specifically, the following experimental methods can be implemented by the above-mentioned electrically assisted turbocharger rotor test bench:

[0056] 1. Static structure and parameter identification experiment:

[0057] (1) Axial preload and contact parameter identification experiment:

[0058] Apply different torques to the shaft end locking nut with a torque wrench to change the axial preload. Use the thrust limit bearing to fix the axial displacement while transmitting the axial preload. Compress the high-speed motor and rotor system as a whole. Place three-phase sensors perpendicular to each other in the middle section to measure the motor vibration. Drill holes on the left and right end covers to place eddy current sensors. Experiments on the dynamic characteristics of the compressor impeller and turbine disk at different speeds are carried out.

[0059] (2) Motor matching form and matching parameter experiment:

[0060] Process multiple motor stators with different inner diameters, and adjust the matching parameters with the central shaft through different matching forms and small clearance matching amount control. Place three-phase sensors perpendicular to each other in the middle section to measure the motor vibration, and punch holes on the left and right end covers to place eddy current sensors to realize the dynamic characteristics experiment of compressor impeller and turbine disk at different speeds;

[0061] 2. Fault experiment:

[0062] (1) Split-type bearing seat hole eccentricity test:

[0063] Adjust the thickness of the gasket installed under the machine base to create misalignment conditions of the central shaft, left machine base, and right machine base; conduct experiments on the dynamic characteristics of the impeller at different speeds, the amplitude of the motor rotor, and the axis trajectory;

[0064] (2) Front and rear impeller imbalance test:

[0065] By adjusting the weight and number of the counterweight bolts on the counterweight plate, the unbalanced mass of the central shaft can be constructed; experiments can be conducted on the dynamic characteristics of the impeller at different speeds, the amplitude of the motor rotor and the axis trajectory;

[0066] The present invention is not limited to the embodiments described above. The above description of the specific embodiments is intended to describe and illustrate the technical solution of the present invention. The above specific embodiments are merely illustrative and not restrictive. Without departing from the scope of the present invention and the scope of protection of the claims, a person of ordinary skill in the art can also make many forms of specific changes under the guidance of the present invention, which all fall within the scope of protection of the present invention.

Claims

1. An electrically assisted turbocharger rotor test bench, characterized in that: The influence of the axial connection structure and assembly process factors are introduced, including a support, a first bearing seat and a second bearing seat are fixed on the left and right sides of the support in a split manner, a compressor wheel seat and a turbine seat are fixed on the outer sides of the first bearing seat and the second bearing seat respectively, a compressor impeller and a turbine disc are installed in the compressor wheel seat and the turbine seat respectively, and a floating ring bearing, a thrust limit bearing and an elastic sealing ring are arranged in the first bearing seat and the second bearing seat for supporting the central rotating shaft; Both ends of the central rotating shaft are fastened by locking nuts, and outer end covers are installed on the outer sides of the compressor wheel seat and the turbine seat. The shaft system sleeve and the motor rotor are connected with clearance fit on the central rotating shaft between the first bearing seat and the second bearing seat; The compressor wheel seat and the turbine seat are both provided with pipeline interfaces and flow guides, and oil film is filled in the floating ring bearing and the thrust limit bearing through the pipeline interfaces and the flow guides; the compressor wheel seat and the turbine seat are both provided with mounting holes for mounting eddy current sensors; A plurality of non-contact displacement sensors are also provided on one side of the central rotating shaft between the first bearing seat and the second bearing seat for measuring the lateral vibration of the entire central rotating shaft.

2. The electrically assisted turbocharger rotor test bench according to claim 1, characterized in that: The front of the central shaft is connected to the first bearing seat through a shaft sleeve, and the rear of the central shaft is directly connected to the second bearing seat; the concentricity and initial static displacement of the central shaft, shaft sleeve and motor rotor are affected by different support forms.

3. The electrically assisted turbocharger rotor test bench according to claim 1, characterized in that: The support is provided with a reference groove, which is used to align the center lines of the compressor wheel seat and the turbine seat with the reference groove during installation to ensure structural centering.

4. The electrically assisted turbocharger rotor test bench according to claim 1, characterized in that: By changing the tightening torque of the locking nut with a torque wrench, the magnitude of the axial preload force and the preload step length can be directly changed, thereby changing the shaft connection stiffness of the central shaft.

5. The electrically assisted turbocharger rotor test bench according to claim 1 or 2, characterized in that: Elastic sealing rings are arranged between the central rotating shaft and the compressor wheel seat and the turbine seat, and two elastic sealing rings are arranged on the central rotating shaft and the turbine seat respectively.

6. The electrically assisted turbocharger rotor test bench according to claim 1, 2 or 5, characterized in that: The central rotating shaft is rotatably connected to the first bearing seat and the second bearing seat through a floating ring bearing; the inner end cover is installed on the opposite side of the first bearing seat and the second bearing seat through a number of fixing bolts; the pre-tightening force of the fixing bolts and the locking nuts can affect the inclination of the axis of the central rotating shaft and affect whether the central rotating shaft is protruding.

7. The electrically assisted turbocharger rotor test bench according to claim 6, characterized in that: The compressor impeller disc and turbine disc are used to simulate the counterweight disc. By adjusting the weight and number of the fixing bolts, the unbalanced state of the central shaft can be simulated.

8. An application of an electrically assisted turbocharger rotor test bench, based on the electrically assisted turbocharger rotor test bench according to any one of claims 1 to 7, characterized in that: Different torques are applied to the locking nut through a torque wrench to change the size of the axial preload. The thrust limit bearing is used to fix the axial displacement while transmitting the axial preload to tighten the shaft system components as a whole. The compressor impeller and turbine disk are machined with scales to obtain static contact deformation. The structural static contact parameter identification experiment is carried out through the relationship between the metal parts processing process parameters. The shaft system components include the shaft system sleeve and the motor rotor.

9. An application of an electrically assisted turbocharger rotor test bench, based on the electrically assisted turbocharger rotor test bench according to any one of claims 1 to 7, characterized in that: Several motor rotors with different inner diameters are processed, and the matching parameters are adjusted through different matching forms and small clearance matching control with the central shaft. The dynamic characteristics experiment of the compressor impeller and turbine disk at different speeds is realized through displacement sensors and eddy current sensors.

10. An application of an electrically assisted turbocharger rotor test bench, based on the electrically assisted turbocharger rotor test bench according to any one of claims 1 to 7, characterized in that: By adjusting the weight and number of the counterweight bolts on the counterweight plate, the unbalanced mass of the central shaft is constructed; experiments are conducted on the dynamic characteristics of the impeller, the amplitude of the motor rotor and the axis trajectory at different speeds to simulate classic faults and assembly problem experiments.

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