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CN114398713B - A method for reducing the knocking noise of a vibration damping decoupler in a vehicle - Google Patents

A method for reducing the knocking noise of a vibration damping decoupler in a vehicle Download PDF

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Publication number
CN114398713B
CN114398713B CN202111328114.5A CN202111328114A CN114398713B CN 114398713 B CN114398713 B CN 114398713B CN 202111328114 A CN202111328114 A CN 202111328114A CN 114398713 B CN114398713 B CN 114398713B
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Prior art keywords
knocking
parameters
vibration damping
decoupler
model
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CN114398713A (en
Inventor
陈敏治
李勤华
童川
张燕
张静文
袁秋华
胡军峰
邓晓龙
刘文强
耿志荣
蓝军
王瑞平
肖逸阁
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Zhejiang Geely Holding Group Co Ltd
Ningbo Geely Royal Engine Components Co Ltd
Aurobay Technology Co Ltd
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Zhejiang Geely Holding Group Co Ltd
Ningbo Geely Royal Engine Components Co Ltd
Aurobay Technology Co Ltd
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    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F30/00—Computer-aided design [CAD]
    • G06F30/10—Geometric CAD
    • G06F30/15—Vehicle, aircraft or watercraft design
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/002—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion characterised by the control method or circuitry
    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F30/00—Computer-aided design [CAD]
    • G06F30/20—Design optimisation, verification or simulation
    • 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
    • Y02T90/00—Enabling technologies or technologies with a potential or indirect contribution to GHG emissions mitigation

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  • General Engineering & Computer Science (AREA)
  • Theoretical Computer Science (AREA)
  • General Physics & Mathematics (AREA)
  • Computer Hardware Design (AREA)
  • Evolutionary Computation (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Acoustics & Sound (AREA)
  • Mechanical Engineering (AREA)
  • Automation & Control Theory (AREA)
  • Computational Mathematics (AREA)
  • Mathematical Analysis (AREA)
  • Mathematical Optimization (AREA)
  • Pure & Applied Mathematics (AREA)
  • Measurement Of Mechanical Vibrations Or Ultrasonic Waves (AREA)

Abstract

本发明提供了一种降低减振解耦器的敲击异响的方法，涉及车辆仿真技术领域。本发明的降低减振解耦器的敲击异响的方法，包括：搭建目标模型；向目标模型中实时输入参数；根据不同时间点下固定参数和载荷参数计算减振解耦器在预设工况下不同时间点的敲击冲量；判断减振解耦器在预设工况下多个敲击冲量中的峰值对应的时间点与实验得到的峰值对应的时间点是否吻合，若吻合，则改变减振解耦器的参数以降低所述敲击冲量的峰值。本发明通过仿真方法来得到减振解耦器的敲击冲量，并通过改变减振解耦器的参数来降低敲击冲量，进而降低减振解耦器的敲击异响，使得减振解耦器的开发周期短、实验的成本低。

The present invention provides a method for reducing the abnormal knocking noise of a vibration damping decoupler, and relates to the field of vehicle simulation technology. The method for reducing the abnormal knocking noise of a vibration damping decoupler of the present invention comprises: building a target model; inputting parameters into the target model in real time; calculating the knocking impulse of the vibration damping decoupler at different time points under preset working conditions according to fixed parameters and load parameters at different time points; judging whether the time point corresponding to the peak value of multiple knocking impulses of the vibration damping decoupler under preset working conditions matches the time point corresponding to the peak value obtained by the experiment, and if so, changing the parameters of the vibration damping decoupler to reduce the peak value of the knocking impulse. The present invention obtains the knocking impulse of the vibration damping decoupler through a simulation method, and reduces the knocking impulse by changing the parameters of the vibration damping decoupler, thereby reducing the abnormal knocking noise of the vibration damping decoupler, so that the development cycle of the vibration damping decoupler is short and the cost of the experiment is low.

Description

Method for reducing knocking abnormal sound of vibration reduction decoupler in vehicle
Technical Field
The invention relates to the technical field of vehicle simulation, in particular to a method for reducing knocking abnormal sound of a vibration reduction decoupler in a vehicle.
Background
At present, in order to damp vibration of an accessory system and a crankshaft system of a vehicle, a vibration damping decoupler is designed in the vehicle. The vibration reduction decoupler has good vibration reduction effect under the working condition of a high-speed large accelerator of a vehicle. However, when the vehicle is in a starting working condition or a small accelerator working condition, the vibration reduction decoupler can play a vibration reduction effect after being matched with the crankshaft system and the accessory system, and meanwhile, the problem of knocking abnormal sound can occur. At present, a test method is mainly adopted for solving the problem of abnormal knocking of the vibration reduction decoupler under the starting working condition or the small accelerator working condition, but the method has long development period of the vibration reduction decoupler, high test cost and high difficulty in checking knocking problems caused by matching among systems because of complex matched systems and changeable working conditions.
Disclosure of Invention
An object of the first aspect of the present invention is to provide a method for reducing rattle of a vibration reduction decoupler in a vehicle, which solves the problems of long development period and high experimental cost of the vibration reduction decoupler in the prior art.
Another object of the first aspect of the present invention is to solve the problem of complexity of the simulation model in the prior art.
In particular, the invention provides a method for reducing the knocking abnormal sound of a vibration reduction decoupler, which is used for reducing the knocking abnormal sound of the vibration reduction decoupler after being matched with an accessory system and a crank shaft system of a vehicle under a preset working condition of the vehicle, wherein the preset working condition comprises a small accelerator working condition or a starting working condition and comprises the following steps:
building a target model;
Inputting parameters into the target model in real time, wherein the parameters comprise fixed parameters and load parameters under the preset working condition, the fixed parameters comprise accessory system parameters, crankshaft system parameters and vibration reduction decoupler parameters, and the load parameters comprise torque and cylinder pressure of the generator under the preset working condition;
Calculating the knocking impulse of the vibration reduction decoupler at different time points under the preset working condition according to the fixed parameters and the load parameters at different time points;
judging whether the calculated time points corresponding to the peak values of the plurality of knocking impulses of the vibration reduction decoupler under the preset working condition are identical to the time points corresponding to the peak values of the plurality of knocking impulses obtained through experiments, and if so, changing the parameters of the vibration reduction decoupler to reduce the peak values of the knocking impulses, so that the knocking abnormal sound of the vibration reduction decoupler is reduced.
Optionally, building the target model includes:
building a standard model, wherein the standard model comprises an accessory system model, a vibration reduction decoupler model and a crankshaft system model;
simplifying the standard model to obtain a simplified model, wherein the accessory system model is simplified to obtain an accessory system one-dimensional plane model, the crankshaft system model is simplified to obtain a crankshaft system one-dimensional torsional vibration model, and the vibration reduction decoupler model is simplified to obtain a vibration reduction decoupler one-dimensional torsional knocking model;
and sequentially connecting the accessory system one-dimensional plane model, the vibration reduction decoupler one-dimensional torsional knocking model and the crankshaft system one-dimensional torsional vibration model to obtain the target model.
Optionally, the step of inputting parameters into the target model includes:
collecting the fixed parameters and the load parameters corresponding to the preset working conditions;
inputting the fixed parameters into the target model;
And inputting corresponding load parameters into the target model under the preset working condition.
Optionally, the step of inputting the fixed parameter into the target model includes:
Inputting the accessory system parameters into the accessory system simplified model, wherein the accessory system parameters comprise the geometric positions and the inertia of a rotating part of a driving water pump, a tensioner, a BSG generator and an air compressor, and the type and the size of a belt;
inputting the crankshaft system parameters into the crankshaft system simplified model, wherein the crankshaft system parameters comprise rigidity and inertia of a belt pulley, a balance shaft, a crankshaft, a dual-mass flywheel and a clutch driving end, and
And inputting vibration reduction decoupler parameters into the vibration reduction decoupler simplified model, wherein the vibration reduction decoupler parameters comprise rigidity, inertia and geometric limit dimensions of relevant components of the vibration reduction decoupler.
Optionally, inputting the corresponding load parameter into the target model under the preset working condition includes:
Inputting torque of the generator into the one-dimensional plane model of the accessory system in the target model under the starting condition, and simultaneously inputting cylinder pressure of the generator into the one-dimensional torsional vibration model of the crankshaft system, or
And under the working condition of the small accelerator, inputting the cylinder pressure of the generator into the one-dimensional torsional vibration model of the crankshaft system.
Optionally, calculating the knocking impulse of the vibration reduction decoupler at different times under the preset working condition according to the fixed parameter and the load parameter includes:
Calculating the spring knocking torque and the knocking speed of the vibration reduction decoupler under the preset working condition according to the fixed parameters and the load parameters;
and multiplying the spring knocking torque and the knocking speed to obtain the knocking impulse.
Optionally, multiplying the spring striking torque and the striking speed to obtain the striking impulse further includes:
Drawing a first curve of the knocking impulse changing along with time, and obtaining a first peak value of the knocking impulse in the first curve and corresponding time;
acquiring and storing a second curve of the knocking impulse, which is obtained through experiments, and obtaining a second peak value of the knocking impulse and corresponding time of the second peak value;
and when the time corresponding to the first peak value is identical to the time corresponding to the second peak value, changing the vibration reduction decoupler parameter to reduce the peak value of the knocking impulse.
Optionally, the step of changing the vibration reduction decoupler parameter to adjust the peak value of the tapping impulse to reduce the tapping abnormal sound of the vibration reduction decoupler comprises:
Changing the vibration damping decoupler parameters input into the target model;
obtaining a third curve of new knocking impulse changing along with time according to the changed vibration reduction decoupler parameters, and obtaining a third peak value of the knocking impulse in the third curve;
and comparing the third peak value with a preset peak value, and storing the changed vibration damping decoupler parameter when the third peak value is smaller than the preset peak value.
The vibration reduction decoupler comprises a large spring, a small spring, a spring shell, a housing, a belt pulley and a driving disc, wherein the number of the large springs is two, the large springs are arranged in the spring shell, two ends of the large springs are abutted by a convex structure in the spring shell, the number of the small springs are two, the small springs are arranged outside the spring shell, two ends of the small springs are abutted by convex matching outside the spring shell, the vibration reduction decoupler parameters comprise large spring parameters and small spring parameters, the large spring parameters comprise the rigidity, the stroke, the center distance and the early warning torque of the large spring, and the small spring parameters comprise the rigidity, the stroke and the center distance of the small spring.
According to the invention, the target model is built, the knocking impulse of the vibration reduction decoupler under the starting working condition or the small accelerator working condition is simulated, the knocking impulse is obtained by inputting the parameters under the corresponding working conditions, the knocking impulse of the vibration reduction decoupler under the starting working condition or the small accelerator working condition can be reduced by changing the parameters, and further the knocking abnormal sound of the vibration reduction decoupler is reduced.
According to the vibration reduction decoupling device, the planar system and the one-dimensional torsion system can be coupled by simplifying the systems and simplifying the systems into the planar system and the one-dimensional torsion system, and whether the vibration reduction decoupling device has knocking risks or not under the transient working condition can be rapidly evaluated.
The above, as well as additional objectives, advantages, and features of the present invention will become apparent to those skilled in the art from the following detailed description of a specific embodiment of the present invention when read in conjunction with the accompanying drawings.
Drawings
Some specific embodiments of the invention will be described in detail hereinafter by way of example and not by way of limitation with reference to the accompanying drawings. The same reference numbers will be used throughout the drawings to refer to the same or like parts or portions. It will be appreciated by those skilled in the art that the drawings are not necessarily drawn to scale. In the accompanying drawings:
FIG. 1 is a time domain noise map and a corresponding time domain noise colormap map of a knock abnormal sound of a vibration reduction decoupler under a small throttle condition;
FIG. 2 is a time domain noise plot and corresponding time domain noise colormap plot of a shock absorber decoupler in a start condition;
FIG. 3 is a schematic flow chart of a method of reducing rattle of a vibration damping decoupler, according to one specific embodiment of the present invention;
FIG. 4 is a schematic flow chart of the steps of building a target model according to a specific embodiment of the invention;
FIG. 5 is a schematic illustration of a simplified representation of a standard accessory system model resulting in a one-dimensional planar model of the accessory system, in accordance with a specific embodiment of the present invention;
FIG. 6 is a schematic illustration of a crankshaft system model simplified to a one-dimensional torsional vibration model of the crankshaft system, in accordance with a particular embodiment of the present invention;
FIG. 7 is a schematic diagram of a simplified vibration damping decoupler model to provide a one-dimensional torsional tap model of the vibration damping decoupler, according to one specific embodiment of the present invention;
FIG. 8 is a schematic diagram of a one-dimensional planar model of an accessory system, a one-dimensional torsional vibration model of a vibration damping decoupler, and a one-dimensional torsional vibration model of a crankshaft system connected in sequence to form a target model according to one specific embodiment of the present invention;
FIG. 9 is a schematic flow chart of the steps of inputting parameters into a target model according to a specific embodiment of the invention;
FIG. 10 is a schematic flow chart of calculating the impact of the vibration reduction decoupler at different times under preset conditions based on fixed parameters and load parameters according to one specific embodiment of the present invention;
FIG. 11 is a schematic flow chart of calculating the impact of the vibration reduction decoupler at different times under preset conditions based on fixed parameters and load parameters, according to one specific embodiment of the present invention;
FIG. 12 is a schematic illustration of a first plot of the rapping impulse of a model vehicle versus time using the vibration reduction decoupler parameters, according to one specific embodiment of the present invention;
FIG. 13 is a schematic flow chart of the steps of varying vibration damping decoupler parameters to adjust the peak value of the tap impulse to reduce the abnormal ringing of the vibration damping decoupler in accordance with one specific embodiment of the present invention;
FIG. 14 is a plot of time domain noise collmap obtained after inputting raw parameters and changing parameters of the vibration reduction decoupler under small throttle conditions;
FIG. 15 is a time domain noise plot obtained after inputting the original parameters and changing the parameters of the vibration damping decoupler during start-up conditions.
Detailed Description
As a specific embodiment of the present invention, the method for reducing the abnormal knocking noise of the vibration reduction decoupler is used for reducing the abnormal knocking noise after the vibration reduction decoupler is matched with the accessory system and the crankshaft system of the vehicle under the preset working condition of the vehicle, wherein the preset working condition includes a small throttle working condition or a starting working condition.
Specifically, in one embodiment, the vibration damping decoupler currently in use may include a large spring, a small spring, a spring shell, a housing, a pulley, and a drive disc. The large springs are arranged in the spring shell, and two ends of the large springs are abutted by the protruding structures in the spring shell. The number of the small springs is two, the small springs are arranged outside the spring shell, and two ends of the small springs are abutted against the protrusions outside the spring shell to be matched. Under the starting working condition of the vehicle, the belt of the vehicle drives the belt pulley to rotate, the belt pulley drives the housing to rotate, the spring housing rotates along with the housing to push the large spring, the large spring pushes the driving disc to move, and the driving disc is connected with the crankshaft of the vehicle, so that torque is transmitted to the engine. Under the acceleration working condition of the vehicle, the crankshaft drives the driving disc to rotate, the driving disc drives the large spring and the large spring to push the spring shell to rotate and compress the small spring, the other end of the small spring presses the housing, the belt pulley is pushed to rotate (the housing and the belt pulley are in interference fit), the housing continues to rotate and compress the small spring until the spring shell contacts with the housing thrust boss, and the driving disc continues to rotate to push the arc-shaped spring to rotate. Under the starting working condition and the small throttle (accelerating) working condition of the vibration reduction decoupler, the rebound of the small spring can cause the knocking of the spring shell and the housing to generate abnormal sound. The large spring stress can also cause knocking abnormal sound between the spring shell and the large spring and between the spring shell and the driving disc. Schematic diagrams of knocking abnormal sound under the starting working condition and the small throttle working condition are shown in fig. 1 and 2. Fig. 1 is a time domain noise map and a corresponding time domain noise coloumap map of the knocking abnormal sound of the vibration reduction decoupler under the starting working condition, and fig. 2 is a time domain noise map and a corresponding time domain noise coloumap map of the knocking abnormal sound of the vibration reduction decoupler under the small throttle working condition. As can be seen from fig. 1 and 2, the vibration damping decoupler has rattle both with small throttle opening and with start opening. In order to reduce the problem of abnormal knocking noise of the vibration reduction decoupler, the aim of reducing the abnormal knocking noise can be achieved by optimizing parameters of the vibration reduction decoupler.
As a specific embodiment of the present invention, referring to fig. 3, the method for reducing the rattle of the vibration damping decoupler according to the present embodiment may include:
Step S100, building a target model;
Step S200, inputting parameters into a target model in real time, wherein the parameters comprise fixed parameters and load parameters under preset working conditions, the fixed parameters comprise accessory system parameters, crankshaft system parameters and vibration reduction decoupler parameters, and the load parameters comprise torque and cylinder pressure of the generator under the preset working conditions.
Step S300, calculating knocking impulse of the vibration reduction decoupler at different time points under a preset working condition according to the fixed parameters and the load parameters at different time points;
Step S400, judging whether the time points corresponding to the peak values in the plurality of knocking impulses of the vibration reduction decoupler obtained through calculation are identical to the time points corresponding to the peak values in the plurality of knocking impulses obtained through experiments under the preset working condition, and if so, changing the parameters of the vibration reduction decoupler to reduce the peak values of the knocking impulses, so that the abnormal knocking sound of the vibration reduction decoupler is reduced.
In the embodiment, the target model is built to simulate the knocking impulse of the vibration reduction decoupler under the starting working condition or the small accelerator working condition, the knocking impulse is obtained by inputting the parameters under the corresponding working conditions, the knocking impulse of the vibration reduction decoupler under the starting working condition or the small accelerator working condition can be reduced by changing the parameters, and further the knocking abnormal sound of the vibration reduction decoupler is reduced.
As a specific embodiment, referring to fig. 4, in step S100 of the present embodiment, building the target model may include:
Step S101, building a standard model, wherein the standard model comprises an accessory system model, a vibration reduction decoupler model and a crankshaft system model. Specifically, in step S101, the accessory system in the present embodiment may include a belt, a driving water pump, a tensioner, a BSG generator, and an air compressor. The crankshaft system may include pistons, connecting rods, crankshafts, DMF (dual mass flywheel), clutch drive ends, and the like. The standard model is a model which is built according to each part and matched with a real object.
Step S102, simplifying the standard model to obtain a simplified model, wherein the accessory system model is simplified to obtain an accessory system one-dimensional plane model, the crankshaft system standard model is simplified to obtain a crankshaft system one-dimensional torsional vibration model, and the vibration reduction decoupler model is simplified to obtain a vibration reduction decoupler one-dimensional torsional knocking model.
In step S102, the standard accessory system model is simplified to obtain an accessory system one-dimensional plane model (see fig. 5), the crankshaft system model is simplified to a crankshaft system one-dimensional torsional vibration model (see fig. 6), the vibration-damping decoupler model is simplified to obtain a vibration-damping decoupler one-dimensional torsional knocking model (see fig. 7), and only torsional vibration is considered by adopting a one-dimensional software mode. The belt in the accessory system model is simplified linearly, the slipping of the belt is not considered, a transient torsional vibration model is built, and the calculation speed is increased (the efficiency is improved by 99%).
In the embodiment, through simplifying each system and simplifying the system into the plane system and the one-dimensional torsion system, the coupling of the plane system and the torsion system can be realized, and whether the vibration reduction decoupler has knocking risk under the transient working condition can be rapidly evaluated.
Step S103, referring to FIG. 8, the accessory system one-dimensional plane model, the vibration reduction decoupler one-dimensional torsional knocking model and the crankshaft system one-dimensional torsional vibration model are sequentially connected to obtain a target model.
In step S103, the purpose of sequentially connecting the accessory system one-dimensional plane model, the vibration reduction decoupler one-dimensional torsional knocking model and the crankshaft system one-dimensional torsional vibration model is to simulate the state that the vibration reduction decoupler is matched with the accessory system and the crankshaft system simultaneously, so that the target system can be closer to the use condition of the actual vibration reduction decoupler, and the simulation accuracy is improved.
As a specific embodiment of the present invention, as shown in fig. 9, in step S200 of the present embodiment, the step of inputting parameters into the object model may include:
step S201, collecting fixed parameters and corresponding load parameters under preset working conditions;
Step S202, inputting fixed parameters into a target model;
Step S203, inputting corresponding load parameters into the target model under the preset working condition.
As a specific embodiment, the step of inputting the fixed parameter into the object model in step S202 may include:
Inputting accessory system parameters into an accessory system simplified model, wherein the accessory system parameters comprise the geometric positions and the inertia of a rotary part of a driving water pump, a tensioner, a BSG generator and an air compressor, and the type and the size of a belt;
Inputting crankshaft system parameters into a crankshaft system simplified model, wherein the crankshaft system parameters comprise rigidity and inertia of a belt pulley, a balance shaft, a crankshaft, a dual-mass flywheel and a clutch driving end, and
And inputting vibration reduction decoupler parameters into the vibration reduction decoupler simplified model, wherein the vibration reduction decoupler parameters comprise rigidity, inertia and geometric limit size of relevant parts of the vibration reduction decoupler.
A fixed parameter is an inherent parameter that does not substantially change over time or with changes in operating conditions. And the accessory systems, the crank shaft systems or the vibration reduction decouplers of different vehicle models or different models have different intrinsic parameters.
As a specific embodiment, in step S203, inputting the corresponding load parameter into the target model under the preset working condition may include:
Inputting torque of a generator into a one-dimensional plane model of an accessory system in a target model under starting working conditions, and simultaneously inputting cylinder pressure of the generator into a one-dimensional torsional vibration model of a crankshaft system, or
And under the working condition of a small accelerator, the cylinder pressure of the generator is input into the one-dimensional torsional vibration model of the crankshaft system.
The load parameters are input as stimuli into the target model. The load parameter may vary over time or with operating conditions.
Among the load parameters, the torque of the BSG motor and the engine starting cylinder pressure are used as boundaries of the starting conditions. From idle to 4000rpm, as a boundary for small throttle conditions.
As a specific embodiment of the present invention, referring to fig. 10, step S300, calculating the striking impulse of the vibration reduction decoupler at different times under the preset working condition according to the fixed parameter and the load parameter may include:
Step S301, calculating the spring knocking torque and knocking speed of the vibration reduction decoupler under a preset working condition according to the fixed parameters and the load parameters;
step S302, the spring knocking torque and the knocking speed are multiplied to obtain knocking impulse.
In this embodiment, the fixed parameter and the load parameter are input to the target model, and then the tapping torque and the tapping speed are calculated, and the tapping impulse is obtained by multiplying the tapping torque and the tapping speed. Because the load parameters are input in time sequence, the obtained knocking torque and knocking speed are output in time sequence, and the finally obtained knocking impulse is output in time sequence and forms a corresponding curve with time.
As a specific embodiment of the present invention, referring to fig. 11, in step S302, multiplying the spring striking torque and the striking speed to obtain the striking impulse may further include:
Step S303, drawing a first curve of the knocking impulse changing along with time, and obtaining a first peak value of the knocking impulse in the first curve and corresponding time;
step S304, a second curve of the knocking impulse, which is obtained through experiments and changes along with time, is obtained and stored, and a second peak value of the knocking impulse in the second curve and the corresponding time are obtained;
In step S305, when the time corresponding to the first peak matches the time corresponding to the second peak, the vibration reduction decoupler parameter is changed to reduce the peak value of the knock impulse.
In this embodiment, in step S303, the vibration damping decoupler has a problem of abnormal knocking noise, so the knocking impulse is continuously changed with time, and in the process of the change, a maximum value, i.e. a first peak value, appears, the peak value indicates the time point in the parameter case, and the knocking situation is the most serious.
In one particular embodiment, the parameters of the vibration reduction decoupler input into the target model may include a large spring parameter including the stiffness, travel, center distance, and early warning torque of the large spring and a small spring parameter including the stiffness, travel, and center distance of the small spring.
Specifically, the partial correlation parameters input into the object model may include data as shown in the following table:
Finally, a first curve of the striking impulse of a certain vehicle model, which is obtained by using the vibration reduction decoupler parameters, is shown in fig. 12.
In step S304, since the vibration damping decoupler also has a rattle during the experiment, the rattle impulse is continuously changed with time, and a maximum value, i.e., the second peak value, is also generated.
In step S305, the purpose of matching the time corresponding to the first peak value and the time corresponding to the second peak value in the present embodiment is to verify whether the target model is correct, and to confirm whether the abnormal knocking noise is generated at a specific portion of the vibration damping decoupler (i.e. the spring back of the small spring may cause the knocking of the spring shell and the housing to generate abnormal noise, and the stress of the large spring may also cause abnormal knocking noise between the spring shell and the large spring, and between the spring shell and the driving disc).
In step S305 in the embodiment, when the time corresponding to the first peak value and the time corresponding to the second peak value coincide, it is explained that the target model of the embodiment is correct, and the knocking abnormal sound is from the specific portion of the vibration reduction decoupler. If the abnormal sound ratio is not matched, the abnormal sound ratio is separated from the specific part, and the abnormal sound ratio cannot be optimized by the method. The embodiment is mainly used for reducing the abnormal sound problem of the specific part of the vibration reduction decoupler, so after the comparison and anastomosis, the peak value of the knocking impulse can be continuously reduced by changing the parameters of the vibration reduction decoupler and inputting the changed parameters into the target model to obtain the knocking impulse, thereby simplifying the knocking abnormal sound of the vibration reduction decoupler.
As a specific embodiment of the present invention, referring to step S400 of the present embodiment, the step of changing the vibration damping decoupler parameter to adjust the peak value of the striking impulse so as to reduce the striking abnormal sound of the vibration damping decoupler may include:
Step S401, changing vibration damping decoupler parameters input into the target model.
In particular, changing the vibration damping decoupler parameter may be performed within the ranges shown in the following figures, thereby continually adjusting the magnitude of the first peak output from the target model.
Parameters (parameters) GEP3 BSG Unit (B)
TVD monomer frequency 320 Hz
HUB (inertia) Within 0.00601+50% of kg.m2
RING 0.0097 kg.m2
BASF 0.0033 kg.m2
Spring shell (Plastic) 0.000403 kg.m2
Small spring rate 0.6 Nm/°
Small spring travel 0/29.5±20% °
The center of the small spring is from the center to the circle center 70.5±20% mm
High spring rate 5.1+2 Times of Nm/°
Large spring mass 130/Root g
Large spring pre-tightening torque 0.5+5 Times Nm
The center of the big spring is from the center to the circle center 60±20% mm
Step S402, a third curve of new knocking impulse changing along with time is obtained according to the changed vibration reduction decoupler parameters, and a third peak value of the knocking impulse in the third curve is obtained.
And S403, comparing the third peak value with a preset peak value, and storing the changed vibration damping decoupler parameters when the third peak value is smaller than the preset peak value.
Because the third peak value obtained after the parameters of the vibration reduction decoupler are changed is not constant with the first peak value, and the second peak value obtained by the actual test cannot be determined, a preset peak value is preset in the application, when the third peak value is smaller than the preset peak value, the problem of abnormal knocking sound of the vibration reduction decoupler under the parameter is smaller, so that the vibration reduction decoupler can be inspected according to the parameter to optimize the performance of the vibration reduction decoupler.
Of course, in actual operation, the smaller the value of the third peak is, the better. In a certain experiment process, the third peak value is stored when being smaller than the preset peak value, and parameters of the vibration reduction decoupler can be continuously updated in a subsequent experiment process, so that the new peak value is compared with the previous smaller peak value, the performance of the vibration reduction decoupler is continuously optimized, and the knocking abnormal sound of the vibration reduction decoupler is reduced as much as possible.
In this embodiment, taking a small throttle condition as an example, a time domain noise colormap obtained after inputting an original parameter and changing a parameter of a vibration reduction decoupler is shown in fig. 14. By the method, the performance of the vibration reduction decoupler can be well optimized, and the knocking abnormal sound of the vibration reduction decoupler is reduced. Taking a starting condition as an example, a time domain noise diagram obtained after inputting original parameters and changing parameters of the vibration reduction decoupler is shown in fig. 15. As can be seen from fig. 15, after the parameters of the vibration reduction decoupler are changed, the rattle noise of the vibration reduction decoupler is significantly reduced.
By now it should be appreciated by those skilled in the art that while a number of exemplary embodiments of the invention have been shown and described herein in detail, many other variations or modifications of the invention consistent with the principles of the invention may be directly ascertained or inferred from the present disclosure without departing from the spirit and scope of the invention. Accordingly, the scope of the present invention should be understood and deemed to cover all such other variations or modifications.

Claims (8)

1.一种降低减振解耦器的敲击异响的方法，用于降低减振解耦器在车辆预设工况下与所述车辆的附件系统和曲轴系统匹配后的敲击异响，其中，所述预设工况包括小油门工况或起动工况，其特征在于，包括：1. A method for reducing the knocking noise of a vibration damping decoupler, for reducing the knocking noise of the vibration damping decoupler after the vibration damping decoupler is matched with the accessory system and crankshaft system of the vehicle under a preset working condition of the vehicle, wherein the preset working condition includes a low throttle working condition or a starting working condition, and is characterized by comprising: 搭建目标模型；Build a target model; 向所述目标模型中实时输入参数，其中，所述参数包括固定参数和所述预设工况下的载荷参数，所述固定参数包括附件系统参数、曲轴系统参数和减振解耦器参数，所述载荷参数包括发电机在所述预设工况下的扭矩和缸压；Inputting parameters into the target model in real time, wherein the parameters include fixed parameters and load parameters under the preset working condition, the fixed parameters include accessory system parameters, crankshaft system parameters and vibration damping decoupler parameters, and the load parameters include torque and cylinder pressure of the generator under the preset working condition; 根据不同时间点下所述固定参数和所述载荷参数计算所述减振解耦器在所述预设工况下不同时间点的敲击冲量；Calculating the knocking impulse of the vibration reduction decoupler at different time points under the preset working condition according to the fixed parameters and the load parameters at different time points; 判断计算得到的所述减振解耦器在所述预设工况下多个敲击冲量中的峰值对应的时间点与实验得到的多个敲击冲量中的峰值对应的时间点是否吻合，若吻合，则改变所述减振解耦器的参数以降低所述敲击冲量的峰值，从而降低所述减振解耦器的敲击异响；Determine whether the calculated time point corresponding to the peak value of the multiple knocking impulses of the vibration damping decoupler under the preset working condition is consistent with the time point corresponding to the peak value of the multiple knocking impulses obtained in the experiment; if they are consistent, change the parameters of the vibration damping decoupler to reduce the peak value of the knocking impulse, thereby reducing the abnormal knocking sound of the vibration damping decoupler; 搭建目标模型包括：Building the target model includes: 搭建标准模型，其中，所述标准模型包括附件系统模型、减振解耦器模型和曲轴系统模型；Building a standard model, wherein the standard model includes an accessory system model, a vibration damping decoupler model and a crankshaft system model; 对所述标准模型进行简化得到简化模型，其中，所述附件系统模型简化后得到附件系统一维平面模型，所述曲轴系统模型简化后得到曲轴系统一维扭振模型，所述减振解耦器模型简化后得到减振解耦器一维扭转敲击模型；The standard model is simplified to obtain a simplified model, wherein the accessory system model is simplified to obtain a one-dimensional plane model of the accessory system, the crankshaft system model is simplified to obtain a one-dimensional torsional vibration model of the crankshaft system, and the vibration damping decoupler model is simplified to obtain a one-dimensional torsional knocking model of the vibration damping decoupler; 将所述附件系统一维平面模型、所述减振解耦器一维扭转敲击模型和所述曲轴系统一维扭振模型依次连接得到所述目标模型。The target model is obtained by sequentially connecting the one-dimensional plane model of the accessory system, the one-dimensional torsional knock model of the vibration damping decoupler and the one-dimensional torsional vibration model of the crankshaft system. 2.根据权利要求1所述的降低减振解耦器的敲击异响的方法，其特征在于，2. The method for reducing the abnormal knocking noise of the vibration damping decoupler according to claim 1, characterized in that: 向所述目标模型中实时输入参数的步骤包括：The step of inputting parameters into the target model in real time comprises: 收集所述固定参数和所述预设工况下对应的所述载荷参数；Collecting the fixed parameters and the corresponding load parameters under the preset working conditions; 向所述目标模型中输入所述固定参数；inputting the fixed parameters into the target model; 在所述预设工况下向所述目标模型中输入对应的载荷参数。The corresponding load parameters are input into the target model under the preset working condition. 3.根据权利要求2所述的降低减振解耦器的敲击异响的方法，其特征在于，3. The method for reducing the abnormal knocking noise of the vibration damping decoupler according to claim 2, characterized in that: 向所述目标模型中输入所述固定参数的步骤包括：The step of inputting the fixed parameters into the target model comprises: 向所述附件系统简化模型中输入所述附件系统参数；其中，所述附件系统参数包括驱动水泵、张紧器、BSG发电机、空压机的几何位置及旋转部分惯量，皮带类型及尺寸；Input the accessory system parameters into the simplified model of the accessory system; wherein the accessory system parameters include the geometric position and rotating part inertia of the driving water pump, tensioner, BSG generator, and air compressor, and the belt type and size; 向所述曲轴系统简化模型中输入所述曲轴系统参数；其中，所述曲轴系统参数包括皮带轮、平衡轴、曲轴、双质量飞轮、离合器主动端的刚度和惯量；和Inputting the crankshaft system parameters into the simplified model of the crankshaft system; wherein the crankshaft system parameters include the stiffness and inertia of the pulley, the balance shaft, the crankshaft, the dual mass flywheel, and the active end of the clutch; and 向所述减振解耦器简化模型中输入减振解耦器参数；其中，所述减振解耦器参数包括减振解耦器相关部件的刚度、惯量和几何限位尺寸。Input the vibration damping decoupler parameters into the simplified model of the vibration damping decoupler; wherein the vibration damping decoupler parameters include the stiffness, inertia and geometric limit size of the relevant components of the vibration damping decoupler. 4.根据权利要求2所述的降低减振解耦器的敲击异响的方法，其特征在于，4. The method for reducing the knocking noise of a vibration damping decoupler according to claim 2, characterized in that: 在所述预设工况下向所述目标模型中输入对应的载荷参数包括：Inputting corresponding load parameters into the target model under the preset working condition includes: 在所述起动工况下向所述目标模型中的所述附件系统一维平面模型中输入所述发电机的扭矩，同时向所述曲轴系统一维扭振模型中输入所述发电机的缸压；或Under the starting condition, inputting the torque of the generator into the one-dimensional plane model of the accessory system in the target model, and inputting the cylinder pressure of the generator into the one-dimensional torsional vibration model of the crankshaft system; or 在所述小油门工况下向所述曲轴系统一维扭振模型中输入所述发电机的缸压。The cylinder pressure of the generator is input into the one-dimensional torsional vibration model of the crankshaft system under the low throttle operating condition. 5.根据权利要求2所述的降低减振解耦器的敲击异响的方法，其特征在于，5. The method for reducing the abnormal knocking noise of the vibration damping decoupler according to claim 2, characterized in that: 根据所述固定参数和所述载荷参数计算所述减振解耦器在所述预设工况下不同时间的敲击冲量包括：Calculating the knocking impulse of the vibration damping decoupler at different times under the preset working condition according to the fixed parameter and the load parameter includes: 根据所述固定参数和所述载荷参数计算所述减振解耦器在所述预设工况下的弹簧敲击扭矩和敲击速度；Calculating the spring knocking torque and the knocking speed of the vibration damping decoupler under the preset working condition according to the fixed parameter and the load parameter; 将所述弹簧敲击扭矩和敲击速度相乘得到所述敲击冲量。The knocking impulse is obtained by multiplying the spring knocking torque and the knocking speed. 6.根据权利要求5所述的降低减振解耦器的敲击异响的方法，其特征在于，6. The method for reducing the abnormal knocking noise of the vibration damping decoupler according to claim 5, characterized in that: 将所述弹簧敲击扭矩和敲击速度相乘得到所述敲击冲量后还包括：After multiplying the spring striking torque and the striking speed to obtain the striking impulse, the following further comprises: 绘制所述敲击冲量随着时间变化的第一曲线，并获得所述第一曲线中敲击冲量的第一峰值及其对应的时间；Draw a first curve showing the change of the knocking impulse over time, and obtain a first peak value of the knocking impulse in the first curve and its corresponding time; 获取并存储实验得到的敲击冲量随时间变化的第二曲线，并获得所述第二曲线中的敲击冲量的第二峰值及其对应的时间；Acquire and store a second curve of the knocking impulse changing with time obtained by the experiment, and obtain a second peak value of the knocking impulse in the second curve and its corresponding time; 在所述第一峰值对应的时间与所述第二峰值对应的时间吻合时，改变所述减振解耦器参数以降低所述敲击冲量的峰值。When the time corresponding to the first peak value coincides with the time corresponding to the second peak value, the vibration reduction decoupler parameters are changed to reduce the peak value of the knocking impulse. 7.根据权利要求6所述的降低减振解耦器的敲击异响的方法，其特征在于，7. The method for reducing abnormal knocking noise of a vibration damping decoupler according to claim 6, characterized in that: 改变所述减振解耦器参数以调整所述敲击冲量的峰值从而降低所述减振解耦器的敲击异响的步骤包括：The step of changing the vibration damping decoupler parameters to adjust the peak value of the knocking impulse and thereby reduce the knocking noise of the vibration damping decoupler comprises: 改变输入至所述目标模型中的所述减振解耦器参数；changing the vibration decoupler parameters input into the target model; 根据改变后的所述减振解耦器参数获得新的敲击冲量随时间变化的第三曲线，并获得所述第三曲线中的敲击冲量的第三峰值；Obtaining a new third curve of the knock impulse changing with time according to the changed parameters of the vibration damping decoupler, and obtaining a third peak value of the knock impulse in the third curve; 将所述第三峰值与预设峰值进行对比，在所述第三峰值小于所述预设峰值时，存储改变后的所述减振震解耦器参数。The third peak value is compared with a preset peak value, and when the third peak value is smaller than the preset peak value, the changed vibration damping decoupler parameter is stored. 8.根据权利要求7所述的降低减振解耦器的敲击异响的方法，其特征在于，所述减振解耦器包括大弹簧、小弹簧、弹簧壳、罩壳、带轮和驱动盘；其中，大弹簧数量为两个，均设置在弹簧壳内，两端均被弹簧壳内的凸起结构抵接；小弹簧数量为两个，均设置在弹簧壳外，两端抵接在弹簧壳外的凸起配合；所述减振解耦器参数包括大弹簧参数和小弹簧参数，所述大弹簧参数包括所述大弹簧的刚度、行程、圆心距和预警扭矩，所述小弹簧参数包括所述小弹簧的刚度、行程和圆心距。8. The method for reducing the abnormal knocking noise of a vibration damping decoupler according to claim 7 is characterized in that the vibration damping decoupler comprises a large spring, a small spring, a spring shell, a cover shell, a pulley and a drive plate; wherein, there are two large springs, both of which are arranged in the spring shell, and both ends are abutted by the protruding structure in the spring shell; there are two small springs, both of which are arranged outside the spring shell, and both ends are abutted against the protrusions outside the spring shell; the vibration damping decoupler parameters include large spring parameters and small spring parameters, the large spring parameters include the stiffness, stroke, center distance and warning torque of the large spring, and the small spring parameters include the stiffness, stroke and center distance of the small spring.
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