CN110261647B - Design method of low-vibration-noise new-energy passenger vehicle motor test bench - Google Patents
Design method of low-vibration-noise new-energy passenger vehicle motor test bench Download PDFInfo
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- G01—MEASURING; TESTING
- G01R—MEASURING ELECTRIC VARIABLES; MEASURING MAGNETIC VARIABLES
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Abstract
The invention provides a design method of a motor test bed of a low-vibration-noise new-energy passenger vehicle, which comprises the following specific processes: establishing a rack model, wherein the rack model comprises a bottom plate, a pair of L-shaped supporting plates, a pair of rear brackets and a vibration isolator system; the L-shaped supporting plate and the rear bracket are arranged on the bottom plate, and the vibration isolator system is arranged below the bottom plate; mounting a test motor and a loading motor on the L-shaped support plate and the rear bracket, and connecting an output shaft of the loading motor with a torque sensor and then with a rotating shaft of the test motor; and setting a target function and constraint conditions, optimizing the structure of the motor rack, and finishing the design of the motor rack. Compared with the prior art, the method can normally perform new energy automobile motor rack performance and NVH tests, and enables the optimized test rack to have the effect of small test rack vibration and noise by setting constraint conditions and objective functions.
Description
Technical Field
The invention belongs to the technical field of new energy automobile tests, and particularly relates to a design method of a low-vibration-noise new energy passenger vehicle motor test bench.
Background
When testers of a new energy automobile motor manufacturer and a new energy automobile passenger car manufacturer build a rack to perform a motor performance test and a motor NVH test under various working conditions, the fact that the motor rack resonates at a certain working condition rotating speed is found, and the test motor easily excites a supporting foundation to resonate in a coupling mode, so that great noise is generated. The main reason for this is that motor manufacturers and automobile manufacturers do not design the motor test bed dynamically, and no effective vibration isolation device is designed between the motor test bed and the supporting foundation.
Disclosure of Invention
The invention aims to overcome the defects of the prior art and provide a design method of a motor test bed of a low-vibration-noise new-energy passenger vehicle, aiming at solving the problem of effectively eliminating vibration noise caused by bed resonance.
The technical scheme of the invention is realized by the following technical scheme:
a design method of a motor test bed of a low-vibration noise new-energy passenger vehicle comprises the following specific processes:
establishing a rack model:
the rack model comprises a bottom plate, a pair of L-shaped supporting plates, a pair of rear brackets and a vibration isolator system; the L-shaped supporting plate and the rear bracket are arranged on the bottom plate, and the vibration isolator system is arranged below the bottom plate; mounting a test motor and a loading motor on the L-shaped support plate and the rear bracket, and connecting an output shaft of the loading motor with a torque sensor and then with a rotating shaft of the test motor;
and setting a target function and constraint conditions, optimizing the structure of the motor rack, and finishing the design of the motor rack.
Further, the objective function of the present invention is: min M, M is the motor rack mass.
Further, the constraint conditions of the invention are as follows:
wherein, Delta1The frequency interval is set for avoiding the motor rack from being connected by two counter-dragging motor rotors and not exciting resonance to the centering excitation frequency;
Δ2the frequency interval is set for avoiding the motor rack from being excited to resonate by the electromagnetic excitation frequency of the motor;
Δ3the frequency interval is set for avoiding the motor rack from being excited to resonate by the periodic electromagnetic field force excitation frequency of the motor stator tooth slot;
nelectric machineIs the rotational speed of the motor;
p is the number of pole pairs of the motor;
and z is the number of slots of the stator of the motor.
Further, the vibration isolator system is composed of a rubber vibration isolator and an air spring.
Further, according to the method, the frequency ratio gamma and the damping ratio zeta of the support system of the rack in the formula (9) are optimized according to an objective function and a constraint condition, and the optimized transfer rate T needs to meet the requirement of being less than or equal to 65%;
furthermore, the horizontal mounting surface of the L-shaped support plate is provided with an adjusting guide groove with a transverse position and a longitudinal position.
Furthermore, the test bench provided by the invention further comprises a laser vibration measurement sensor and a flow field air gap noise sensor, wherein the laser vibration measurement sensor is arranged on the sensor bracket, and the flow field air gap noise sensor is fixed on the test motor.
Advantageous effects
Compared with the prior art, the method can normally perform new energy automobile motor rack performance and NVH tests, and enables the optimized test rack to have the effect of small test rack vibration and noise by setting constraint conditions and objective functions.
The horizontal mounting surface of the L-shaped support plate is provided with the adjusting guide groove with the transverse position and the longitudinal position, the assembly is convenient before the bench test, the shaft centering precision of the motor rotor and the torque sensor is high, and the vibration excitation caused by the misalignment of the motor rotor is effectively avoided.
The test bench provided by the invention also comprises a laser vibration measurement sensor and a flow field air gap noise sensor, so that the normal vibration noise test can be carried out, and the axle center track and the air gap noise of the rotor can be tested.
Drawings
FIG. 1 is a diagram of a motor test bed according to an embodiment of the present invention (10 rubber vibration isolation blocks are used at the bottom);
FIG. 2 is a diagram of a motor test bed (4 air springs are used at the bottom);
FIG. 3 is a vibration isolation curve of a motor test bed under various working conditions.
Fig. 4 is a basic vibration isolation mechanical model of the motor.
Detailed Description
The following describes in detail embodiments of the method of the present invention with reference to the accompanying drawings.
In order to make the objects, technical solutions and advantages of the embodiments of the present invention clearer, the technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention.
The embodiment of the invention discloses a design method of a motor test bed of a low-vibration-noise new-energy passenger vehicle, which comprises the following specific steps of:
step one, completing basic design of a low vibration noise motor NVH test bed.
The rack model comprises a bottom plate, a pair of L-shaped supporting plates, a pair of rear brackets and a vibration isolator system; the L-shaped supporting plate and the rear bracket are arranged on the bottom plate, and the vibration isolator system is arranged below the bottom plate; the test motor and the loading motor are arranged on the L-shaped supporting plate and the rear bracket, and an output shaft of the loading motor is connected with the torsion sensor and then connected with a rotating shaft of the test motor.
Specifically, the method comprises the following steps: the horizontal mounting surface of the L-shaped support plate is carved with an adjusting guide slot with a transverse position and a longitudinal position, a vibration isolator system is mounted below the bottom plate and comprises a rubber vibration isolator and an air spring, a pair of L-shaped support plates are fixed on the bottom plate through adjusting slots on the horizontal mounting surface, a pair of rear brackets are respectively mounted on the horizontal mounting surfaces of the L-shaped support plates, the front end of a loading motor is fixed on an opening of one L-shaped support plate, the rear end of the loading motor is supported by the rear bracket, the front end of a testing motor is fixed on the opening of the other L-shaped support plate, and the rear end of the testing motor is; the torque sensor is arranged on an output shaft of the loading motor and is connected with a rotating shaft of the testing motor.
The rack is convenient to assemble, the transverse position and longitudinal position adjusting guide grooves are arranged on the bottom plate, the laser centering device is combined, the test motor rotor, the loading motor rotor and the torque sensor shaft are conveniently centered, the centering precision is high, and vibration excitation caused by misalignment of the motor rotor is effectively avoided.
The test bench provided by the embodiment of the invention is also provided with a sensor bracket for supporting the laser vibration measurement sensor, and the flow field air gap noise sensor is fixed on a test motor. The test bench provided by the embodiment of the invention can test the axle center track and air gap noise of the motor rotor as shown in figure 2, besides normal motor performance and vibration noise test, due to the arrangement of the pair of laser vibration measurement sensors and the flow field air gap noise sensor.
Establishing a test motor-torque sensor-loading motor-supporting L plate-bottom plate-vibration isolator system model by using three-dimensional software, guiding the model into finite element software, carrying out grid division, calculating the vibration mode of the motor test bench system, and optimizing according to the following objective function and constraint conditions:
objective function Min M (quality)
In the above formula: m is the mass of the motor stand;
Δ1to avoid the motor rack being connected by two counter-dragging motor rotors to be not centeredA frequency interval in which the excitation frequency excites resonance;
Δ2the frequency interval is set for avoiding the motor rack from being excited to resonate by the electromagnetic excitation frequency of the motor;
Δ3the frequency interval is set for avoiding the motor rack from being excited to resonate by the periodic electromagnetic field force excitation frequency of the motor stator tooth slot;
nelectric machineIs the rotational speed of the motor or motors,
nelectric machine＝1000rpm,2000rpm,3000rpm,4000rpm,5000rpm,6000rpm,7000rpm,
8000rpm,9000rpm,10000rpm；
p is the number of pole pairs of the motor;
z is the number of stator slots.
And optimizing the structure of the motor rack by adopting a genetic algorithm according to the objective function and the constraint condition. The finite element simulation result of the optimized rack shows that: the six-order rigid body modal vibration frequency of the designed motor test bed system is respectively as follows: 3.46Hz (horizontal translation of the whole rack), 3.53Hz (horizontal translation of the rack), 5.22Hz (swing of the rack around the Z axis), 8.29Hz (vertical jump of the rack up and down), 9.25Hz (swing of the rack around the X axis) and 10.39Hz (swing of the rack around the Y axis); in addition, the first order to the eighth order elastic modal frequencies of the motor test bench are respectively as follows: 200.71Hz (baseplate bending vibration), 293.07Hz (baseplate torsion vibration), 372.00Hz (two L plates are in same direction bending vibration), 390.90Hz (rotor radial breathing vibration), 394.92Hz (two L supporting plates are in opposite direction torsion vibration), 472.6Hz (two L supporting plates are in same direction torsion vibration), 486.42Hz (two L supporting plates are in opposite direction bending vibration) and 529.00 Hz.
When the motor is tested in the rotating speed range of 0-10000rpm, the natural frequencies cannot be excited by various vibration exciting forces, and the normal performance of the motor performance and NVH test is ensured.
And step three, designing and optimizing a rubber vibration isolator and an air spring between the bottom plate of the motor test bed and the foundation, so that the vibration isolation system can effectively attenuate vibration energy.
At the moment, the motor is a vibration source, and the purpose of the vibration isolation device is to reduce the influence of the motor vibration on the foundation and the environment. Fig. 4 is a diagram of a force vibration isolation model. Let the excitation force generated by motor m be
F＝F0cosωt (2)
Wherein, F0The amplitude of the exciting force of the motor is shown, and omega represents the circular frequency of the exciting force.
The vibration equation of the motor m is
Where x represents the motor gantry vibrational displacement response.
Let the solution of the equation be
x＝X cos(ωt-ψ) (4)
Where ψ represents a phase difference and X represents a vibration displacement amplitude.
Substituting the above formula into (3) to obtain
Wherein k represents the gantry support system stiffness; beta represents a gantry support system dynamic factor; gamma represents the gantry support system frequency ratio gamma, and zeta represents the gantry support system damping ratio;
obtaining the force amplitude of the vibration source by the formula (5)
And the load transferred to the bottom foundation by the motor vibration source has two:
1) spring force: fk＝kx＝kX cos(ωt-ψ)
2) Damping force:
where c represents the gantry support system damping coefficient.
The resultant force amplitude of the above two forces is
Defining the force transmission rate:
substituting (7) into the above formula to obtain
The vibration isolation rate of the motor bottom vibration isolation system is as follows:
η＝1-T
the gantry support system frequency ratio γ and the damping ratio ζ in equation (9) are optimized according to the optimization objective function and the constraint condition. The rigidity of 10 rubber vibration isolators between the base plate of the optimized motor test bed and the foundation is 110N/mm; the rigidity of 4 air springs is 80N/mm, and the air pressure of the air bags is 4 bar. The vibration isolator design can ensure that the vibration isolation rate of the test bench under the conditions of connection misalignment vibration excitation, motor electromagnetic vibration excitation and stator tooth space period electromagnetic field force vibration excitation of the test motor, the torque sensor and the loading motor shaft under various rotating speed working conditions reaches more than 52% (except that the vibration isolation rate of the test bench under the rotating speed of 1000rpm of the motor is 36.30%), effectively eliminates the resonance problem of the test bench and the foundation during the NVH test of the motor, and ensures the normal operation of the NVH test of the motor, as shown in figure 3.
Therefore, the problem of vibration noise caused by the resonance of the motor test bed of the new energy passenger car is solved/realized.
In summary, the above description is only a preferred embodiment of the present invention, and is not intended to limit the scope of the present invention. Any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.
Claims (5)
1. A design method of a motor test bed of a low-vibration-noise new-energy passenger vehicle is characterized by comprising the following specific processes:
establishing a rack model:
the rack model comprises a bottom plate, a pair of L-shaped supporting plates, a pair of rear brackets and a rack supporting vibration isolation system; the L-shaped support plate and the rear bracket are arranged on the bottom plate, and the rack support vibration isolation system is arranged below the bottom plate; mounting a test motor and a loading motor on the L-shaped support plate and the rear bracket, and connecting an output shaft of the loading motor with a torque sensor and then with a rotating shaft of the test motor;
setting a target function and constraint conditions, and optimizing the structure of the motor test bed to complete the design of the motor test bed;
the objective function is: min M, M is the quality of the motor rack;
the constraint conditions are as follows:
wherein, Delta1The frequency interval is set for avoiding the motor test bed from being excited to resonate by the connection of two counter-dragging motor rotors and the centering excitation frequency;
Δ2the frequency interval is set for avoiding the motor test bed from being excited to resonate by the electromagnetic excitation frequency of the motor;
Δ3the frequency interval is set for avoiding the motor test bench from being excited to resonate by the periodic electromagnetic field force excitation frequency of the motor stator tooth slot;
nelectric machineIs the rotational speed of the motor;
p is the number of pole pairs of the motor;
and z is the number of slots of the stator of the motor.
2. The design method of the low-vibration noise new-energy passenger vehicle motor test bench according to claim 1, wherein the bench support vibration isolation system is composed of a rubber vibration isolator and an air spring.
3. The design method of the motor test bed of the low-vibration noise new-energy passenger vehicle according to claim 2, characterized in that according to an objective function and a constraint condition, a frequency ratio gamma and a damping ratio zeta of a bed support vibration isolation system in the formula (9) are optimized, and a transfer rate T after optimization is less than or equal to 65%;
wherein, FTThe resultant force amplitude, F, being transmitted from the source of vibration of the motor to the base0The excitation force amplitude of the motor is shown.
4. The design method of the motor test bed of the low-vibration noise new-energy passenger vehicle as claimed in claim 1, wherein the horizontal mounting surface of the L-shaped support plate is engraved with adjusting guide grooves of transverse position and longitudinal position.
5. The design method of the motor test bed of the low-vibration-noise new-energy passenger vehicle according to claim 1, wherein the motor test bed further comprises a laser vibration measurement sensor and a flow field air gap noise sensor, the laser vibration measurement sensor is mounted on a sensor bracket, and the flow field air gap noise sensor is fixed on a test motor.
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| CN114509276B (en) * | 2022-01-19 | 2024-04-19 | 深圳市大地和电气股份有限公司 | Efficient control method for eliminating abnormal sound and improving electric NVH performance of rack |
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