CN119803890A - An electrically assisted turbocharger rotor test bench and its application - Google Patents
An electrically assisted turbocharger rotor test bench and its application Download PDFInfo
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- CN119803890A CN119803890A CN202411923488.5A CN202411923488A CN119803890A CN 119803890 A CN119803890 A CN 119803890A CN 202411923488 A CN202411923488 A CN 202411923488A CN 119803890 A CN119803890 A CN 119803890A
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
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Abstract
The invention discloses an electric auxiliary turbocharger rotor experiment table and application, which can realize static contact parameter identification experiment, dynamic characteristic and parameter matching relation experiment of an electric auxiliary turbocharger through axial lock nuts, thrust bearings, floating ring bearing support shafting structures, equivalent compressor blades, turbine disc simulation masses and middle motor structure driving. According to the invention, the axial locking device is used for fixing the shafting component, the tightening torque and the tightening step length are adjusted to change the pre-tightening parameter, and the static contact parameter is identified by combining the metal processing technological parameter. And the equivalent simulation counterweight disc is arranged on the central rotating shaft, and the weight and the number of the counterweight bolts are adjusted to simulate rotor unbalance and typical assembly fault experiments.
Description
Technical Field
The invention relates to the technical field of turbocharger experiment tables, in particular to a novel electric auxiliary turbocharger rotor experiment table considering a connecting structure and an assembling process and application thereof.
Background
With the development of the automobile industry and internal combustion engines, exhaust gas turbocharging technology is widely applied to engine design by virtue of advantages of the technology in the aspects of fuel economy benefit, exhaust emission environmental protection, engine performance improvement and the like. However, due to the influence of the problems of variable load environment, severe working environment, obvious hysteresis effect and the like, the rotor system of the turbocharger is easy to generate faults such as fatigue failure, overspeed damage and the like. In order to solve the engineering problems of the traditional turbocharger, a high-speed motor auxiliary turbocharger design is generated. The design of the novel electric auxiliary turbocharger needs to consider more complex shafting assembly structure and assembly process errors, which can cause problems of prominent overall vibration problem, vibration damage of part of components and the like. The initial structure of the rotor system can be changed by introducing and assembling the motor, so that uncertainty exists in structural vibration response, along with the prominence of vibration problems, the contact state between shaft system matching parts can be changed during processing and assembling, the contact nonlinearity can have a great influence on the vibration characteristics of the rotor system, and the parameter uncertainty caused by a connecting structure can also bring challenges to the dynamic design of the supercharger structure. The overall vibration characteristics are highly dependent on axial pretension assembly parameter variations, shafting component assembly process effects, and stability effects.
However, the laboratory bench in the prior art has the following problems:
1. in the prior art, the experiment table generally simplifies shafting components in a large range, and the matching forms and the matching parameters of the sleeve, the rotating shaft, the motor and the rotating shaft are ignored, or the shafting components are integrally designed on the central rotating shaft after being subjected to simple mass and rotational inertia equivalence.
2. Because the whole traditional experiment table adopts an integrated design method, no precise experiment table processing method exists, so that the contact effect between axial parts is completely ignored, and the existing experiment table can not develop experimental research and test aiming at the contact characteristics of the rotor experiment table under different working conditions.
3. In the electric auxiliary booster experiment table, the driving mode is that an external motor is connected with a central rotating shaft through a coupler, the position of the original high-speed motor is simplified into an equivalent disc through the design of the rotating shaft, the structure ignores the influence of the coupling of the motor and a rotor system, and the influence of the assembly problem between the motor and the rotor system on the performance of the system is ignored.
4. The pretension has a significant impact on the performance of the system. The pretightening force and the assembly clearance are affected by the step length and the step number in the bolt tightening process, the rotation speed of the rotating shaft and other factors. It exhibits a complex evolution trend under different operating conditions of rest, low speed or high speed. In particular, under the working conditions of overrun vibration and the like caused by high-speed rotation of the rotating shaft, the parameter relation of the pre-tightening force of the bolt, the number of tightening steps, the tightening step length, the axial structure clearance, the amplitude deviation of the rotor and the like needs to be analyzed. The existing experiment table can not meet the requirements.
Disclosure of Invention
The invention aims to overcome the defects in the prior art, solve the problems that a laboratory bench in the prior art is difficult to consider the influence of component contact effect change and assembly process factors under the high rotating speed or working rotating speed margin, and provide an electric auxiliary turbocharger rotor laboratory bench and application, which are mainly used for simulating static contact parameter identification and dynamic characteristic experiment of a complex combined rotor shafting structure under the problems of typical rotor faults and assembly.
The experiment table synthesizes the existing finish machining process, the integral machining process of the traditional rotor experiment table is decomposed into different shafting combined parts, the contact forms and contact parameters among different shafting parts are considered, and the initial static displacement of the rotor experiment table is controlled, so that the rotor structure static parameters considering the contact effect can be effectively identified. Meanwhile, the bearing seat is processed in a split mode to realize the introduction of the central motor of the electric auxiliary turbocharger, and the influence of the split bearing and the assembly mode of the central motor is considered to effectively measure the dynamic characteristics of the rotor system. The physical parameters of the impeller and the turbine disc of the air compressor are equivalent, the complicated curved blade profile is simplified, and meanwhile, the additional counterweight bolts on the counterweight disc can be repeatedly disassembled and assembled to simulate the unbalance faults of the impeller and the rotor. Under the comprehensive consideration of the connection contact effect and the influence of the assembly process, the novel structural design of the traditional electric auxiliary booster rotor experiment table realizes the design of the multi-factor multifunctional coupling novel rotor experiment table.
The invention aims at realizing the following technical scheme:
the electric auxiliary turbocharger rotor experiment table comprises a support, wherein a first bearing seat and a second bearing seat are fixed on the left side and the right side of the support in a split mode, a compressor wheel seat and a turbine wheel seat are respectively fixed on the outer sides of the first bearing seat and the second bearing seat, a compressor impeller and a turbine disc are respectively installed in the compressor wheel seat and the turbine wheel seat, and floating ring bearings, thrust limiting bearings and elastic sealing rings are arranged in the first bearing seat and the second bearing seat and used for supporting a central rotating shaft;
Both ends of the central rotating shaft are fastened through locking nuts, outer end covers are arranged on the outer sides of the compressor wheel seat and the turbine wheel seat, and a shafting sleeve and a motor rotor are connected to the central rotating shaft between the first bearing seat and the second bearing seat in a clearance fit manner;
the compressor wheel seat and the turbine seat are respectively provided with a pipeline interface and a flow guide channel, and oil films are filled in the floating ring bearing and the thrust limit bearing through the pipeline interfaces and the flow guide channels;
And one side of the central rotating shaft between the first bearing seat and the second bearing seat is also provided with a plurality of non-contact displacement sensors for measuring the integral transverse vibration of the central rotating shaft.
Furthermore, the front part of the central rotating shaft is connected with the first bearing seat through the shafting sleeve, the rear part of the central rotating shaft is directly connected with the second bearing seat, and the concentricity and initial static displacement of the central rotating shaft, the shafting sleeve and the motor rotor are influenced through different support forms.
Further, a reference groove is formed in the support and used for enabling the center line of the compressor wheel seat and the center line of the turbine wheel seat to be aligned with the reference groove during installation, so that structural centering is ensured.
Further, the tightening torque of the lock nut is changed through the torque wrench, and the magnitude of the axial pre-tightening force and the pre-tightening step length are directly changed, so that the shafting connection rigidity of the central rotating shaft is changed.
Further, elastic sealing rings are arranged between the central rotating shaft and the compressor wheel seat and between the central rotating shaft and the turbine wheel seat, and the two elastic sealing rings are respectively arranged on the central rotating shaft and the turbine wheel seat.
Furthermore, the central rotating shaft is rotationally connected with the first bearing seat and the second bearing seat through floating ring bearings, inner end covers are arranged on the opposite sides of the first bearing seat and the second bearing seat through a plurality of fixing bolts, and the pretightening force of the fixing bolts and the locking nuts can influence the axis inclination of the central rotating shaft and influence whether the central rotating shaft is in an axon or not.
Further, the compressor impeller disc and the turbine disc are used for simulating a counterweight disc, and the weight and the number of the fixing bolts are adjusted to simulate an unbalanced state of the central rotating shaft.
The invention also provides an application of the electric auxiliary turbocharger rotor experiment table, which comprises the steps of applying torques of different magnitudes to the lock nut through a torque wrench, changing the magnitude of axial pretightening force, transmitting the axial pretightening force while fixing axial displacement through a thrust limit bearing, integrally compacting a shafting part, processing scales on a compressor impeller and a turbine disc, obtaining static contact deformation, and carrying out a structure static contact parameter identification experiment through the relation of metal piece processing technological parameters, wherein the shafting part comprises a shafting sleeve and a motor rotor.
The invention also provides application of the electric auxiliary turbocharger rotor experiment table, a plurality of motor rotors with different inner diameters are processed, the mode of adjusting the matching parameters is realized through different matching modes and control of small clearance matching quantity with the central rotating shaft, and the characteristic experiment of the compressor impeller and the turbine disk movement under different rotating speeds is realized through the displacement sensor and the electric vortex sensor.
The invention also provides an application of the electric auxiliary turbocharger rotor experiment table, wherein the unbalanced mass of the central rotating shaft is constructed by adjusting the weight and the number of the counterweight bolts on the counterweight disc, and experiments of impeller dynamic characteristics, motor rotor amplitude and axle center track under different rotating speeds are carried out to simulate classical faults and assembly problem experiments.
Compared with the prior art, the technical scheme of the invention has the following beneficial effects:
1. the invention controls the fit clearance of the motor rotating shaft by a precision machining technology, and can develop experimental study of structural vibration characteristics of various radial fit forms and fit parameters. By careful consideration of the complex shafting structure, the response precision and experimental efficiency of the contact effect on the dynamic characteristics of the rotor system are remarkably improved.
2. The invention utilizes the shaft end locking nut and the split-type processing bearing seat, and researches the influence of the process variables on the static characteristics (such as the deflection deformation of the axis to the neutral and the rotating shaft) and the dynamic characteristics (such as the rotating disc, the motor vibration amplitude and the axis track) of the central rotating shaft by adjusting the pretightening force, the tightening step number, the step length and other parameters of the fixing bolt connected with the support. And experimental basis is provided for revealing the influence of assembly process factors on the vibration characteristics of the rotor system.
3. Unbalance simulation and fault experiment function, namely, a balance weight disc arranged on a central rotating shaft can simulate the unbalance state of the rotating shaft by adjusting the number and the weight of the balance weight bolts. The experiment table can simulate dynamic characteristic experiments such as impeller dynamic characteristics, motor amplitude, axle center track and the like at different rotating speeds, effectively reproduces and researches the influence of assembly process and typical faults on system performance, and further promotes fault diagnosis and optimal design of a supercharger rotor system.
4. And (3) identifying static parameters of the contact effect, namely accurately identifying the static contact parameters in the complex combined rotor shafting structure through the matching form of the shafting sleeve and the floating ring bearing which are independently designed by the experiment table. The influence of the contact nonlinearity, the assembly clearance and other variables on the static characteristics is comprehensively analyzed, and the structural design and process adjustment of the electric auxiliary turbocharger are facilitated to be optimized.
5. The multi-factor coupling research platform successfully realizes the multi-function integration and multi-factor coupling research of the novel experiment table through the introduction of the split bearing seat and the middle motor assembly form and the equivalence of physical parameters of the compressor impeller and the turbine disc, and provides a reliable experiment platform for analyzing complex contact and assembly effects under high rotation speed margin.
6. The test bench is provided with a plurality of non-contact displacement sensors and eddy current sensors, so that the transverse vibration and dynamic response of the center rotating shaft can be accurately measured. And the assembling forms and the operating conditions under different working conditions are combined, so that the capability of measuring and experimental analysis of the dynamic characteristics of the rotor system of the supercharger is further improved.
Drawings
FIG. 1 is a schematic diagram of the overall side view of the rotor test stand of the present invention.
Fig. 2 is a sectional view taken along the direction B-B in fig. 1.
Fig. 3 is an axial cross-sectional view of the seal structure.
Fig. 4 is a schematic structural view of a single split machined bearing housing.
Fig. 5 is a front cross-sectional view of a single split machined bearing housing.
Fig. 6 is a cross-sectional view of a single split machined bearing housing from a top view.
Fig. 7 is a cross-sectional view of the shafting sleeve.
The reference numerals are 1, a support, 2, a compressor wheel seat, 3, a lock nut, 4, a compressor impeller, 5, an elastic sealing ring, 6, a thrust limit bearing, 7, a floating ring bearing, 8, a turbine seat, 9, a turbine disk, 10, a central rotating shaft, 11, a pipeline interface, 12, a motor rotor, 13, a shafting sleeve, 14, an inner end cover, 15, a first bearing seat, 16, a turbine, 17, an outer end cover and 18-second bearing seat
Detailed Description
The present invention will be described in further detail with reference to the drawings and examples, in order to make the objects, technical solutions and advantages of the present invention more apparent. It should be understood that the specific embodiments described herein are for purposes of illustration only and are not intended to limit the scope of the invention. In addition, the technical features of the embodiments of the present invention described below may be combined with each other as long as they do not collide with each other.
As shown in fig. 1 and 2, the embodiment provides an electric auxiliary turbocharger rotor experiment table, which introduces the effects of an axial connection structure and assembly process factors, and comprises a support 1, wherein a first bearing seat 15 and a second bearing seat 18 are fixed on the left side and the right side of the support 1 in a split mode, a compressor wheel seat 2 and a turbine seat 8 are respectively fixed on the outer sides of the first bearing seat 15 and the second bearing seat 18, a compressor impeller 4 and a turbine disk 9 are respectively installed in the compressor wheel seat and the turbine seat for avoiding air turbulence, and are respectively connected with the first bearing seat and the second bearing seat into a whole through fixing bolts, and a diversion volute system for simulating the positions of the compressor impeller 4 and the turbine disk 9 is arranged in a split mode. The first bearing seat 15 and the second bearing seat 18 are respectively internally 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, and the central motor is coupled with the rotor system to simulate the electric auxiliary characteristic under the high-speed motor.
Both ends of the central rotating shaft 10 are fastened through locking nuts 3, outer end covers 17 are arranged on the outer sides of the compressor wheel seat 2 and the turbine wheel seat 8, and a shafting sleeve 13 and a motor rotor 12 are connected to the central rotating shaft 10 between the first bearing seat 15 and the second bearing seat 18 in a clearance fit manner;
The air compressor wheel seat 2 and the turbine seat 8 are respectively provided with a pipeline interface 11 and a flow guide channel, oil films are filled in the floating ring bearing 7 and the thrust limit bearing 6 through the pipeline interfaces and the flow guide channels, the air compressor wheel seat 2 and the turbine seat 8 are respectively provided with a mounting hole for mounting an eddy current sensor, the eddy current sensor is mounted on the magnetic suction seat and is fixed on the support through the magnetic suction seat, and the probe extends into the mounting holes for non-contact measurement.
A plurality of non-contact displacement sensors are further arranged on one side of the central rotating shaft 10 between the first bearing seat 15 and the second bearing seat 18 and used for measuring the overall transverse vibration of the central rotating shaft. The displacement sensor is fixed on the support and connected with the front-end processor, and the probe is close to the central rotating shaft to perform non-contact measurement.
Specifically, the counterweight disc simulating the compressor impeller 4 in the compressor wheel seat 2 is axially preloaded by the lock nut 3 through a threaded connection locking device, the right side limits the integral axial displacement through the thrust limit bearing 6, axial force is transmitted to a shafting sleeve structure connected with the floating ring bearing 7, and the motor rotor 12 is integrally preloaded at the right part of the central rotating shaft. The combined shafting structure can take the contact effect between the parts and the change of the contact effect in a high-rotating-speed working condition and a working rotating speed margin interval into consideration. The turbine mount 8 is likewise limited by a simulated turbine weight plate via a lock nut and thrust bearing. The pipeline interfaces 11 and the guide channels arranged on the left bearing seat and the right bearing seat can guide lubricating oil through the oil pump in the working state, and provide a proper working environment for the floating ring bearing.
Preferably, the front part of the central shaft 10 is connected to the first bearing housing 15 through the shafting sleeve 13, the rear part of the central shaft 10 is directly connected to the second bearing housing 18, and concentricity and initial static displacement of the central shaft 10, shafting sleeve 13 and motor rotor 12 are affected by different support forms.
Preferably, the support 1 is provided with a reference groove for aligning the midlines of the compressor wheel mount 2 and the turbine mount 8 with the reference groove when mounted to ensure structural centering.
Preferably, the tightening torque of the lock nut 3 is changed through a torque wrench, and the magnitude of the axial pre-tightening force and the pre-tightening step length are directly changed, so that the shafting connection rigidity of the central rotating shaft 10 is changed.
Preferably, elastic sealing rings are arranged between the central rotating shaft and the compressor wheel seat and between the central rotating shaft and the turbine wheel seat, the two elastic sealing rings are respectively arranged on the central rotating shaft and the turbine wheel seat, the central rotating shaft is rotationally connected with the first bearing seat and the second bearing seat through floating ring bearings, inner end covers 14 are arranged on the opposite sides of the first bearing seat and the second bearing seat through a plurality of fixing bolts, the pretightening force of the fixing bolts and the locking nuts 3 can influence the axis inclination of the central rotating shaft to influence whether the central rotating shaft is in an axon or not, a counterweight disc is further arranged on the central rotating shaft 10, a plurality of counterweight bolts are detachably connected to the counterweight disc, and the unbalanced state of the central rotating shaft is simulated by adjusting the weight and the number of the counterweight bolts.
Referring to fig. 1, the axial assembly details of the compressor wheel mount and turbine wheel mount and the radial mating details of the shafting components are shown. The split bearing seat is connected with the support 1 through a fixing bolt, is connected with the turbine seat through a hexagonal bolt in the axial direction, and is sleeved with a clearance fit sleeve structure and a motor rotor structure outside the central rotating shaft 10.
Fig. 3 shows a sealing structure, and by means of the elastic sealing ring 5 and the sealing end cover, the operation of the thrust limit bearing and the floating ring bearing can provide proper oil pressure and oil sealing performance.
Fig. 4 shows an elevation view of a single split machined bearing housing. The bearing pedestal and the bearing end cover are provided with a plurality of flow guide ports in different directions, the bearing pedestal and the bearing end cover can be connected with a pipeline interface to provide an oil path environment, and meanwhile, the sensor can be stretched inwards after punching to measure oil film pressure, temperature and lubrication parameters.
FIG. 5 shows a cross-sectional view of a bearing housing, which provides space for an oil path through a flow guide port and a flow guide channel, and is communicated with a floating ring bearing and a thrust limit bearing, so as to provide a proper working environment, and meanwhile, an external sealing structure is used for preventing the leakage of lubricating oil.
Fig. 6 shows a sectional view of the bearing housing in a top view, showing the form of connection of the bearing housing to the turbine housing, by means of a long bolt fixing bolt, while showing the structure of the elastic sealing ring.
Fig. 7 shows a cross-section of the whole shafting sleeve 13, the left end is required to be connected with the floating ring bearing 7 and the inner end cover 14 on the first bearing seat 15, a small-scale concave exists, and the right end is in pressing contact with the motor rotor.
Specifically, the following experimental mode can be realized through the above-mentioned electrically assisted turbocharger rotor experiment table:
1. static structure and parameter identification experiment:
(1) Axial pretension and contact parameter identification experiment:
The torque wrench is used for applying different torques to the shaft end locking nut, the axial pretightening force is changed, the thrust limit bearing is used for fixing axial displacement, the axial pretightening force is transmitted, the high-speed motor and the rotor system are integrally compressed, the three-phase sensor which is mutually perpendicular is placed in the middle section for motor vibration measurement, the eddy current sensor is placed in the left end cover and the right end cover in a punching mode, and therefore the compressor impeller and turbine disc movement characteristic experiment under different rotating speeds is achieved;
(2) Motor matching form and matching parameter experiment:
Processing a plurality of motor stators with different inner diameters, controlling the motor stators and a central rotating shaft through different matching modes and small clearance matching quantity, realizing the mode of adjusting matching parameters, placing mutually vertical three-phase sensors in the middle section for motor vibration measurement, punching holes on left and right end covers, placing eddy current sensors, and realizing the dynamic characteristic experiment of a compressor impeller and a turbine disk at different rotating speeds;
2. fault experiment:
(1) And (3) split type bearing seat hole machining concentricity experiment:
adjusting the thickness of the gasket arranged under the machine base to construct the misalignment working conditions of the central rotating shaft, the left machine base and the right machine base, and carrying out experiments on the dynamic characteristics of the impeller, the amplitude of the motor rotor and the axis locus at different rotating speeds;
(2) Front-rear impeller imbalance experiment:
the unbalanced mass of the central rotating shaft is constructed by adjusting the weight and the number of the counterweight bolts on the counterweight disc, so that experiments on the dynamic characteristics of the impeller, the amplitude of the motor rotor and the axis locus at different rotating speeds can be carried out;
The invention is not limited to the embodiments described above. The above description of specific embodiments is intended to describe and illustrate the technical aspects of the present invention, and is intended to be illustrative only and not limiting. Numerous specific modifications can be made by those skilled in the art without departing from the spirit of the invention and scope of the claims, which are within the scope of the invention.
Claims (10)
1. The electric auxiliary turbocharger rotor experiment table is characterized by comprising a support, wherein the influence of an axial connection structure and assembly process factors is introduced, a first bearing seat and a second bearing seat are fixed on the left side and the right side of the support in a split mode, a compressor wheel seat and a turbine wheel seat are respectively fixed on the outer sides of the first bearing seat and the second bearing seat, a compressor impeller and a turbine disc are respectively installed in the compressor wheel seat and the turbine wheel seat, and floating ring bearings, thrust limiting bearings and elastic sealing rings are arranged in the first bearing seat and the second bearing seat and used for supporting a central rotating shaft;
Both ends of the central rotating shaft are fastened through locking nuts, outer end covers are arranged on the outer sides of the compressor wheel seat and the turbine wheel seat, and a shafting sleeve and a motor rotor are connected to the central rotating shaft between the first bearing seat and the second bearing seat in a clearance fit manner;
the compressor wheel seat and the turbine seat are respectively provided with a pipeline interface and a flow guide channel, and oil films are filled in the floating ring bearing and the thrust limit bearing through the pipeline interfaces and the flow guide channels;
And one side of the central rotating shaft between the first bearing seat and the second bearing seat is also provided with a plurality of non-contact displacement sensors for measuring the integral transverse vibration of the central rotating shaft.
2. The electric auxiliary turbocharger rotor laboratory bench of claim 1, wherein the front portion of the central shaft is connected to the first bearing housing via a shafting sleeve, the rear portion of the central shaft is directly connected to the second bearing housing, and concentricity and initial static displacement of the central shaft, shafting sleeve and motor rotor are affected by different support forms.
3. An electrically assisted turbocharger rotor bench according to claim 1 wherein said support is provided with a datum recess for aligning the compressor wheel mount and turbine wheel mount midlines with the datum recess during installation to ensure structural centering.
4. The electrically assisted turbo charger rotor laboratory bench of claim 1, wherein the magnitude of the axial preload and the preload step are directly varied by varying the tightening torque of the lock nut by the torque wrench, thereby varying the shafting connection stiffness of the central spindle.
5. An electrically assisted turbo charger rotor laboratory bench according to claim 1 or 2, wherein elastic sealing rings are arranged between the central spindle and the compressor wheel seat and turbine wheel seat, and two elastic sealing rings are arranged on the central spindle and turbine wheel seat respectively.
6. The electric auxiliary turbocharger rotor experiment table according to claim 1, 2 or 5, wherein the central rotating shaft is rotatably connected with the first bearing seat and the second bearing seat through floating ring bearings, inner end covers are arranged on the opposite sides of the first bearing seat and the second bearing seat through a plurality of fixing bolts, and the pretightening force of the fixing bolts and the locking nuts can influence the axis inclination of the central rotating shaft and influence whether the central rotating shaft is in an axon or not.
7. The electrically assisted turbo charger rotor laboratory bench of claim 6, wherein the compressor impeller disk and turbine disk are configured to simulate a counterweight disk by adjusting the weight and number of the fixing bolts to simulate an imbalance condition of the central spindle.
8. An application of an electric auxiliary turbocharger rotor experiment table is based on the electric auxiliary turbocharger rotor experiment table according to any one of claims 1-7, and is characterized in that torque with different magnitudes is applied to a lock nut through a torque wrench, the magnitude of axial pretightening force is changed, axial displacement is fixed through a thrust limit bearing, the axial pretightening force is transmitted, a shafting part is integrally compressed, scales are machined on a compressor impeller and a turbine disc, static contact deformation can be obtained, structural static contact parameter identification experiments are conducted through the relation of metal part machining process parameters, and the shafting part comprises a shafting sleeve and a motor rotor.
9. An application of an electric auxiliary turbocharger rotor experiment table based on any one of claims 1-7, characterized in that a plurality of motor rotors with different inner diameters are processed, the form of adjusting the matching parameters is realized through controlling different matching forms and small clearance matching amount with a central rotating shaft, and the dynamic characteristic experiment of a compressor impeller and a turbine disc under different rotating speeds is realized through a displacement sensor and an electric vortex sensor.
10. An application of an electric auxiliary turbocharger rotor experiment table based on any one of claims 1-7 is characterized in that unbalanced mass of a central rotating shaft is built by adjusting weight and number of counterweight bolts on a counterweight disc, experiments of impeller dynamic characteristics, motor rotor amplitude and axle center track at different rotating speeds are carried out, and classical fault and assembly problem experiments are simulated.
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