CN112966403A - Method for reducing automobile brake noise - Google Patents
Method for reducing automobile brake noise Download PDFInfo
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
- B60T17/00—Component parts, details, or accessories of power brake systems not covered by groups B60T8/00, B60T13/00 or B60T15/00, or presenting other characteristic features
- B60T17/002—Air treatment devices
- B60T17/008—Silencer devices
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Abstract
The invention discloses a method for reducing automobile brake noise, which comprises the steps of establishing a three-dimensional model of a brake, establishing a finite element model, carrying out finite element analysis and obtaining a region R of the brake noisesDetermining the allowable range of values of the friction coefficient mu and the contact rigidity K between the brake discs meeting the performance requirement of the braking system to form a rectangular region RpAnalyzing the graph, and adjusting the range of the friction coefficient mu and the contact rigidity K to reduce the region RpAnd region RsThe brake noise is suppressed, and the like. Has the advantages that: the invention can effectively reduce the occurrence probability of the brake noise by reducing the brake noise from the design level, thereby not only improving the comfort of the vehicle, but also improving the comfort of the vehicleThe noise pollution to the environment is reduced, the service life deterioration of the brake system parts caused by friction noise is reduced, and the vehicle brake performance is improved.
Description
Technical Field
The invention relates to a noise reduction method, in particular to a method for reducing automobile brake noise, and belongs to the technical field of automobile noise reduction.
Background
With the rapid development of the automobile industry, the automobile keeping amount in China increases year by year, and the requirements of people on the safety, comfort and environmental protection of automobiles are higher and higher. The problem of brake noise in the automobile industry has become one of the most complaints among customers, and the negative effects of brake noise include the effect on riding comfort, the serious pollution of noise to the environment, the effect on the service life of brake system components and the like.
At present, the solution to the problem of brake noise is mainly to reduce noise in the vehicle by using a passive sound insulation and absorption method, but the influence of brake noise on the environment and the influence on the service life of parts of a brake system cannot be solved.
Currently, there is also research on active noise reduction by improving the relevant structural dimensions of the components of the brake and optimizing the material structural parameters of the brake pads. However, a relatively sophisticated evaluation scale has not been developed to measure the conditions that can be satisfied by the relevant parameters of the system to avoid or reduce the occurrence of brake noise.
Disclosure of Invention
The purpose of the invention is as follows: aiming at the defects in the prior art, the invention provides a method for reducing the braking noise of an automobile by optimizing the friction coefficient and the contact rigidity between a brake disc and a brake block; the invention improves the driving comfort of the vehicle, reduces the noise influence on the environment, reduces the service life deterioration of the parts of the braking system caused by friction noise and improves the braking performance of the vehicle.
The technical scheme is as follows: a method of reducing brake noise in a vehicle, comprising the steps of:
step one, establishing a three-dimensional model of a brake;
step two, establishing a finite element model and carrying out finite element analysis: importing the three-dimensional model of the brake into finite element software, generating a finite element model by setting material properties of parts, dividing grids and establishing a contact relation, and carrying out complex modal analysis on the finite element model to obtain a complex characteristic value;
step three, obtaining a region R of the brake noises: repeatedly calculating the complex characteristic value by modifying the friction coefficient mu between the brake discs and the rigidity K of the spring unit, obtaining the range of the friction coefficient mu and the contact rigidity K corresponding to the positive real part alpha of the complex characteristic value lambda, and obtaining the range of the contact rigidity KRegion R of brake noises；
Step four, determining the allowable range of values of the friction coefficient mu and the contact rigidity K between the brake discs meeting the performance requirement of the braking system to form a rectangular region Rp；
Step five, chart analysis: the area R is divided by taking the friction coefficient mu as an abscissa and the contact rigidity K as an ordinatepAnd region RsExpressed in the same coordinate, the critical coefficient of friction at the occurrence of brake noise is μc；
Step six, adjusting the range of the friction coefficient mu and the contact rigidity K to reduce the region RpAnd region RsOverlap area A (R)p∩Rs) And the suppression of brake noise is realized.
The rectangular area R in the sixth steppAnd region RsOverlap area A (R)p∩Rs) The magnitude of (A) represents the probability of occurrence of brake noise, and R is reduced in the brake design processpAnd RsTo achieve suppression of brake noise.
Preferably, the brake in the first step is a disc brake, and the structure of the disc brake comprises a brake disc and a brake pad.
Preferably, the material properties of the parts in the second step include density, young's modulus and poisson's ratio.
Preferably, the establishing of the contact relationship in the second step is to establish a spring unit at the corresponding node between the brake discs, and replace the contact stiffness between the brake discs and the node of the brake pad unit with the stiffness of the spring unit.
Preferably, in the third step, the contact stiffness K is n × K, n is the number of nodes, K is the stiffness of the spring unit, and the value of the stiffness K of the spring unit is determined according to the magnitude of the braking pressure.
Preferably, the friction coefficient mu between the brake discs in the fourth step is 0.25-0.70.
Preferably, the allowable range of the contact stiffness K in the fourth step is determined according to the positive pressure of the brake block and the displacement between the disc blocks, and the contact stiffness K is as follows:
in the formula, F is the positive pressure of the brake block; d is the normal relative displacement of the brake disc and the brake pad.
Preferably, the region R is reduced in the sixth steppAnd region RsOverlap area A (R)p∩Rs) The method can be known according to the chart analysis of the step five:
the first method is to reduce the friction coefficient mu between brake discs on the premise of ensuring the braking performance, so that a rectangular region R is formedpMoving to the left, an overlapping area A (R) is achievedp∩Rs) The value range of the friction coefficient mu is smaller than the critical friction coefficient mu of the brake noisecWhile, the overlapping area A (R)p∩Rs)＝0；
Secondly, the contact rigidity K between the brake disc blocks is reduced by adjusting the structure of the brake system, so that the region RsTo realize the overlapping area A (R)p∩Rs) To a critical coefficient of friction mu of the noisecWhen the value range of the friction coefficient mu is larger than the value range of the system, the overlapping area A (R) is realizedp∩Rs)＝0。
Has the advantages that: the method for reducing the brake noise from the design level can effectively reduce the occurrence probability of the brake noise, thereby not only improving the comfort of the vehicle, but also reducing the noise pollution to the environment, reducing the deterioration of the service life of the parts of the brake system caused by the friction noise and improving the brake performance of the vehicle.
Drawings
FIG. 1 is a flow chart of a method of the present invention;
FIG. 2 is a pre-design analysis of noise reduction in accordance with the present invention;
FIG. 3 is a noise reduction design analysis graph optimized for coefficient of friction according to the present invention;
FIG. 4 is an analysis of a noise reduction design optimized for contact stiffness according to the present invention;
in the figure:
1 is the range R of the variation of the friction coefficient and the contact rigidityp(ii) a 2 is the region R where braking noise occurss(ii) a 3 is a critical friction coefficient mu when braking noise occursc。
Detailed Description
The invention will be further described with reference to the following figures and specific examples, but the scope of the invention is not limited thereto.
A method of reducing brake noise in a vehicle, comprising the steps of:
step one, establishing a three-dimensional model of a brake;
step two, establishing a finite element model and carrying out finite element analysis: importing the three-dimensional model of the brake into finite element software, generating a finite element model by setting material properties of parts, dividing grids and establishing a contact relation, and carrying out complex modal analysis on the finite element model to obtain a complex characteristic value;
step three, obtaining a region R of the brake noises: repeatedly calculating a complex characteristic value by modifying the friction coefficient mu between the brake discs and the rigidity K of the spring unit, obtaining the range of the friction coefficient mu and the contact rigidity K corresponding to the positive real part alpha of the complex characteristic value lambda, and obtaining the region R of the brake noises；
Step four, determining the allowable range of values of the friction coefficient mu and the contact rigidity K between the brake discs meeting the performance requirement of the braking system to form a rectangular region Rp；
Step five, chart analysis: the area R is divided by taking the friction coefficient mu as an abscissa and the contact rigidity K as an ordinatepAnd region RsExpressed in the same coordinate, the critical coefficient of friction at the occurrence of brake noise is μc；
Step six, adjusting the range of the friction coefficient mu and the contact rigidity K to reduce the region RpAnd region RsOverlap area A (R)p∩Rs) And the suppression of brake noise is realized.
The rectangular area R in the sixth steppAnd region RsOverlap area A (R)p∩Rs) Is representative of brake noiseProbability of occurrence, R reduction in brake designpAnd RsTo achieve suppression of brake noise.
According to the method for reducing the automobile braking noise, the friction coefficient mu and the contact rigidity K between the brake disc and the brake pad have important influence on the braking noise, so that the correlation between the friction coefficient mu and the contact rigidity K of the brake disc and the brake pad and the generation of the braking noise are established, and the system is enabled to avoid the noise generation condition by adjusting the friction coefficient mu and the contact rigidity K of the brake system. In the noise reduction method, the friction coefficient mu meets the requirement of the automobile braking performance, the national standard specifies the automobile brake block, and the value range of the friction coefficient mu of the disc brake meets 0.25-0.7. The allowable range of the contact stiffness K between the brake pads is determined according to the positive pressure of the brake pad and the displacement between the brake pads, and is represented by the following formula:
in the formula (I); f is the positive pressure borne by the brake block; d is the normal relative displacement of the brake disc and the brake pad. The range of the contact rigidity between the brake discs can be obtained by inquiring the maximum braking force of the vehicle and the minimum relative displacement between the brake discs.
Importing the three-dimensional model of the selected disc brake into finite element software in the finite element software, generating the finite element model by setting material properties of parts, dividing grids, establishing a contact relation and the like, repeatedly calculating parameters such as friction coefficient mu between brake disc blocks and spring unit rigidity k and the like to perform complex mode analysis complex eigenvalue, obtaining the range of the friction coefficient and the contact rigidity corresponding to the real part alpha of the complex eigenvalue lambda as positive time, and forming a region R with brake noises. The area R is defined by the coefficient of friction mu as the abscissa and the contact stiffness K as the ordinatepAnd region RsAre shown in the same coordinates.
The rectangular region RpAnd region RsOverlap area A (R)p∩Rs) Representing the probability of noise occurrence, the smaller the areaEnsuring R in the brake design process as the probability of brake noise occurrence is smallerpAnd RsOverlap area A (R)p∩Rs) As small as possible to achieve suppression of brake noise, and ideally, A (R)p∩Rs) 0 indicates that no noise is present, and the overlap region a (R) described in the present invention is overlappedp∩Rs) The method of (2) to minimize the area includes two implementations.
As shown in fig. 1 and 3, the first design method is to adjust relevant structural parameters of a brake disc and a brake pad on the premise of ensuring the braking performance, so that the value of the friction coefficient μ of the system is reduced, and the rectangular area R is accordingly formedpMoving to the left to ensure that the value range of the friction coefficient mu is less than the critical friction coefficient mucRealizing the overlapping area A (R)p∩Rs) 0, thereby avoiding the occurrence of braking noise.
As shown in fig. 1 and 4, the second design method is to reduce the contact stiffness K between the brake pads by adjusting the structure of the brake system, and the reduction of the contact stiffness K reduces the real part of the complex eigenvalue in the system equation, thereby reducing the unstable mode with the positive real part, and reducing the region RsSo that the critical friction coefficient mu of the noisecGreater than the coefficient of friction mu of the system, the overlap region A (R) is achievedp∩Rs) 0, thereby avoiding the occurrence of braking noise.
The above description is only a preferred embodiment of the present invention and is not intended to limit the scope of the present invention, it should be understood that any modification, improvement or equivalent substitution made by those skilled in the art will fall within the scope of the present invention without departing from the spirit and spirit of the present invention.
Claims (8)
1. A method of reducing brake noise in a vehicle, comprising the steps of:
step one, establishing a three-dimensional model of a brake;
step two, establishing a finite element model and carrying out finite element analysis: importing the three-dimensional model of the brake into finite element software, generating a finite element model by setting material properties of parts, dividing grids and establishing a contact relation, and carrying out complex modal analysis on the finite element model to obtain a complex characteristic value;
step three, obtaining a region R of the brake noises: repeatedly calculating a complex characteristic value by modifying the friction coefficient mu between the brake disc and the brake block and the rigidity K of the spring unit, obtaining the range of the friction coefficient mu and the contact rigidity K corresponding to the positive real part alpha of the complex characteristic value lambda, and obtaining the region R of the brake noises；
Step four, determining the allowable range of values of the friction coefficient mu and the contact rigidity K between the brake discs meeting the performance requirement of the braking system to form a rectangular region Rp；
Step five, chart analysis: the area R is divided by taking the friction coefficient mu as an abscissa and the contact rigidity K as an ordinatepAnd region RsExpressed in the same coordinate, the critical coefficient of friction at the occurrence of brake noise is μc；
Step six, adjusting the range of the friction coefficient mu and the contact rigidity K to reduce the region RpAnd region RsOverlap area A (R)p∩Rs) And the suppression of brake noise is realized.
2. The method for reducing braking noise of an automobile according to claim 1, wherein: the brake in the step one is a disc brake, and the structure of the brake comprises a brake disc and a brake block.
3. The method for reducing braking noise of an automobile according to claim 1, wherein: and the material properties of the parts in the second step comprise density, Young modulus and Poisson ratio.
4. The method for reducing braking noise of an automobile according to claim 2, wherein: and step two, establishing the contact relation, namely establishing a spring unit on a corresponding node between the brake disc blocks, and replacing the contact rigidity between the brake disc and the brake block unit node with the rigidity of the spring unit.
5. The method for reducing braking noise of an automobile according to claim 4, wherein: and in the third step, the contact stiffness K is n multiplied by K, n is the node number, K is the stiffness of the spring unit, and the value of the stiffness K of the spring unit is determined according to the magnitude of the brake pressure.
6. The method for reducing braking noise of an automobile according to claim 1, wherein: and the friction coefficient mu between the brake discs in the fourth step ranges from 0.25 to 0.70.
7. The method for reducing braking noise of an automobile according to claim 1, wherein: the allowable range of the contact stiffness K in the fourth step is determined according to the positive pressure of the brake block and the displacement between the disc blocks, and the contact stiffness K is as follows:
in the formula, F is the positive pressure of the brake block; d is the normal relative displacement of the brake disc and the brake pad.
8. The method for reducing braking noise of vehicle according to claim 1, wherein the region R is reduced in the sixth steppAnd region RsOverlap area A (R)p∩Rs) The method can be known according to the chart analysis of the step five:
the first method is to reduce the friction coefficient mu between brake discs on the premise of ensuring the braking performance, so that a rectangular region R is formedpMoving to the left, an overlapping area A (R) is achievedp∩Rs) The value range of the friction coefficient mu is smaller than the critical friction coefficient mu of the brake noisecWhile, the overlapping area A (R)p∩Rs)＝0；
Secondly, the contact rigidity K between the brake disc blocks is reduced by adjusting the structure of the brake system, so that the region RsTo realize the overlapping area A (R)p∩Rs) To a critical coefficient of friction mu of the noisecWhen the value range of the friction coefficient mu is larger than the value range of the system, the overlapping area A (R) is realizedp∩Rs)＝0。
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010087711.2A CN112966403B (en) | 2020-02-11 | Method for reducing automobile brake noise |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010087711.2A CN112966403B (en) | 2020-02-11 | Method for reducing automobile brake noise |
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| Publication Number | Publication Date |
|---|---|
| CN112966403A true CN112966403A (en) | 2021-06-15 |
| CN112966403B CN112966403B (en) | 2024-06-07 |
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Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP3124819A1 (en) * | 2015-07-31 | 2017-02-01 | Peugeot Citroën Automobiles SA | Method for optimising a brake system in order to reduce the crunching noise |
| CN107544284A (en) * | 2017-07-20 | 2018-01-05 | 同济大学 | Automotive brake frictional noise control method under a kind of complex conditions |
| CN110726571A (en) * | 2019-08-22 | 2020-01-24 | 上海大陆汽车制动系统销售有限公司 | Test and evaluation method for brake noise under automobile steering condition |
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP3124819A1 (en) * | 2015-07-31 | 2017-02-01 | Peugeot Citroën Automobiles SA | Method for optimising a brake system in order to reduce the crunching noise |
| CN107544284A (en) * | 2017-07-20 | 2018-01-05 | 同济大学 | Automotive brake frictional noise control method under a kind of complex conditions |
| CN110726571A (en) * | 2019-08-22 | 2020-01-24 | 上海大陆汽车制动系统销售有限公司 | Test and evaluation method for brake noise under automobile steering condition |
Non-Patent Citations (1)
| Title |
|---|
| 余为高;于学华;: "应用有限元法对盘式制动器制动噪声分析", 科学技术与工程, no. 12, 15 June 2009 (2009-06-15) * |
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