CN113255084A - Rapid optimization method of gear noise radiation based on response surface method - Google Patents

Rapid optimization method of gear noise radiation based on response surface method Download PDF

Info

Publication number
CN113255084A
CN113255084A CN202110764678.7A CN202110764678A CN113255084A CN 113255084 A CN113255084 A CN 113255084A CN 202110764678 A CN202110764678 A CN 202110764678A CN 113255084 A CN113255084 A CN 113255084A
Authority
CN
China
Prior art keywords
gear
shell
calculating
response
variable
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
CN202110764678.7A
Other languages
Chinese (zh)
Other versions
CN113255084B (en
Inventor
赵培龙
高晓光
马宏刚
刘敦宁
苑衍灵
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Shengrui Transmission Co Ltd
Original Assignee
Shengrui Transmission Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Shengrui Transmission Co Ltd filed Critical Shengrui Transmission Co Ltd
Priority to CN202110764678.7A priority Critical patent/CN113255084B/en
Publication of CN113255084A publication Critical patent/CN113255084A/en
Application granted granted Critical
Publication of CN113255084B publication Critical patent/CN113255084B/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F30/00—Computer-aided design [CAD]
    • G06F30/10—Geometric CAD
    • G06F30/17—Mechanical parametric or variational 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
    • F16H—GEARING
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/02—Toothed members; Worms
    • F16H55/14—Construction providing resilience or vibration-damping
    • F16H55/16—Construction providing resilience or vibration-damping relating to teeth only
    • 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
    • G06F30/27—Design optimisation, verification or simulation using machine learning, e.g. artificial intelligence, neural networks, support vector machines [SVM] or training a model
    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F2119/00—Details relating to the type or aim of the analysis or the optimisation
    • G06F2119/10—Noise analysis or noise optimisation
    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F2119/00—Details relating to the type or aim of the analysis or the optimisation
    • G06F2119/14—Force analysis or force optimisation, e.g. static or dynamic forces

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Geometry (AREA)
  • Theoretical Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • General Physics & Mathematics (AREA)
  • Evolutionary Computation (AREA)
  • Computer Hardware Design (AREA)
  • Medical Informatics (AREA)
  • Software Systems (AREA)
  • Computer Vision & Pattern Recognition (AREA)
  • Artificial Intelligence (AREA)
  • Mechanical Engineering (AREA)
  • Computational Mathematics (AREA)
  • Mathematical Analysis (AREA)
  • Mathematical Optimization (AREA)
  • Pure & Applied Mathematics (AREA)
  • Gears, Cams (AREA)
  • Testing Of Devices, Machine Parts, Or Other Structures Thereof (AREA)

Abstract

The invention relates to a method for quickly optimizing gear noise radiation based on a response surface method, which comprises the following steps of: s1: calculating time-varying meshing stiffness of gear set by using gear parameter variables
Figure 133511DEST_PATH_IMAGE001
(ii) a S2: according to time-varying mesh stiffness
Figure 581810DEST_PATH_IMAGE001
Calculating gear mesh excitation force generated by gear
Figure 892705DEST_PATH_IMAGE002
(ii) a S3: establishing a finite element analysis model of the gearbox shell, and calculating the gear engagement exciting force obtained in the step S2
Figure 819073DEST_PATH_IMAGE002
Applying the vibration response to the shell, and calculating the vibration response of the surface of the shell; s4: extracting the surface mesh of the shell finite element model in the step S3, and mapping the shell vibration response to the surface mesh of the shell, thereby calculating the radiation noise y at the sound pressure level of one meter according to the direct boundary element method; s5: constructing a first-order response surface model with a gear parameter variable as an input variable and a one-meter sound pressure level radiation noise y as an output; s6: optimizing gear parameter variables according to the first-order response surface model; the variable tooth number, modulus, displacement coefficient and tooth width can be quickly optimized.

Description

Rapid optimization method of gear noise radiation based on response surface method
Technical Field
The invention relates to the technical field of transmissions, in particular to a method for quickly optimizing gear noise radiation based on a response surface method.
Background
The transmission is an important part widely applied to mechanical transmission, and gear radiation noise is an important index influencing the performance of the transmission. When gears are meshed, because errors such as tooth pitch and tooth profile inevitably exist, meshing impact is generated in the running process, noise corresponding to the meshing frequency of the gears is generated, and friction noise is generated between tooth surfaces due to relative sliding. The gear is a basic part in transmission, and reduction of gear noise is necessary for controlling transmission noise. The traditional gear radiation noise optimization optimizes the gear by repeatedly calling a finite element model, and the optimization efficiency is low.
Therefore, there is a need to develop a method for rapidly optimizing gear radiation noise.
Disclosure of Invention
The invention aims to solve the technical problem of providing a method for quickly optimizing gear radiation noise based on a response surface method, which can quickly optimize gear parameters and improve optimization efficiency after a response surface model of the gear parameters and the gear radiation noise is established.
In order to solve the technical problems, the technical scheme of the invention is as follows: a method for quickly optimizing gear noise radiation based on a response surface method comprises the following steps:
s1: determining gear parameter variables, and calculating the time-varying meshing stiffness of the gear set by using the gear parameter variables
Figure 253831DEST_PATH_IMAGE001
；
S2: time-varying meshing stiffness according to step S1
Figure 969721DEST_PATH_IMAGE001
Calculating gear mesh excitation force generated by gear
Figure 973449DEST_PATH_IMAGE002
；
S3: establishing a finite element analysis model of the gearbox shell, and calculating the gear engagement exciting force obtained in the step S2
Figure 618057DEST_PATH_IMAGE002
Applying the vibration response to the shell, and calculating the vibration response of the surface of the shell;
s4: extracting the surface mesh of the shell finite element model in the step S3, and mapping the shell vibration response to the surface mesh of the shell, thereby calculating the radiation noise y at the sound pressure level of one meter according to the direct boundary element method;
s5: constructing a first-order response surface model with a gear parameter variable as an input variable and a one-meter sound pressure level radiation noise y as an output;
s6: and optimizing the gear parameter variables according to the first-order response surface model in the step S5.
As a preferable technical scheme, in step S1, calculating the time-varying meshing stiffness of the gear set according to a Weber-Banaschek gear stiffness calculation method
Figure 340025DEST_PATH_IMAGE001
。
Preferably, in step S1, the gear parameter variables include tooth number z, module m, and shift coefficient
Figure 95491DEST_PATH_IMAGE003
And a tooth width b.
Preferably, in step S3, the gear is engaged with the exciting force
Figure 688147DEST_PATH_IMAGE002
Applied to the housing bearing seats.
Preferably, step S5 includes the following steps:
s51: determining gear parameter variables and tolerance ranges;
s52: determining a plurality of groups of gear parameter variable values according to the gear parameter variable and the tolerance range;
s53: executing the steps S1 to S4, and calculating the response value of the gear one-meter sound pressure level radiation noise corresponding to each group of gear parameter variable values;
s54: and obtaining the relation between the input variable and the output variable by utilizing the variable value of each group of gear parameters and the response value of the gear one-meter sound pressure level radiation noise corresponding to the variable value of each group of gear parameters.
As a preferable technical solution, in step S6, the variable tooth number, modulus, displacement coefficient, and tooth width are optimized by using a genetic algorithm with the goal of minimizing the radiation noise y at a sound pressure level of one meter.
A first-order response surface model of gear parameters and the radiation noise of the shell at the sound pressure level of one meter is constructed by a quick optimization method of the gear radiation noise based on a response surface method; by utilizing the first-order response surface model, the variable tooth number, the modulus, the displacement coefficient and the tooth width can be quickly optimized, and the problem of low calculation efficiency of repeatedly calling a finite element model in the traditional optimization is solved.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly described below, and it is obvious that the drawings in the following description are only some embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to these drawings without creative efforts.
FIG. 1 is a flow chart of the present invention;
FIG. 2 is a single tooth force diagram;
FIG. 3 is a schematic illustration of a vibration velocity data map.
Detailed Description
A method for quickly optimizing gear noise radiation based on a response surface method comprises the following steps:
s1: determining gear parameter variables, wherein the gear parameter variables comprise tooth number z, modulus m and deflection coefficient
Figure 769235DEST_PATH_IMAGE003
Tooth width b;
inputting the gear parameter variables, and calculating the time-varying meshing stiffness of the gear set according to the Weber-Banaschek gear stiffness calculation method
Figure 214385DEST_PATH_IMAGE001
。
Time varying mesh stiffness
Figure 773543DEST_PATH_IMAGE001
Is calculated as follows:
Figure 751863DEST_PATH_IMAGE004
in the formula,
Figure 472694DEST_PATH_IMAGE005
in order to achieve the single tooth stiffness of the gear wheel 1,
Figure 903676DEST_PATH_IMAGE006
is the single tooth stiffness of the gear 2.
The calculation of the single tooth stiffness k is as follows:
Figure 945DEST_PATH_IMAGE007
in the formula,
Figure 99351DEST_PATH_IMAGE008
as to the total amount of deformation of the gear teeth,
Figure 495478DEST_PATH_IMAGE009
is a normal load; the stress analysis of the gear is shown in fig. 2, and the single-tooth stiffness of the gear 1 and the single-tooth stiffness of the gear 2 can be respectively calculated according to the formula.
Total deflection of gear teeth
Figure 413755DEST_PATH_IMAGE008
Is calculated as follows:
Figure 580294DEST_PATH_IMAGE010
in the formula,
Figure 2048DEST_PATH_IMAGE011
in order to be able to bend the gear wheel 1 in shear,
Figure 330262DEST_PATH_IMAGE012
shear deformation for bending of the gear 2;
Figure 735835DEST_PATH_IMAGE013
in order to deform the tooth basis of the gear wheel 1,
Figure 440486DEST_PATH_IMAGE014
is the tooth base deformation of the gear 2;
Figure 483791DEST_PATH_IMAGE015
is deformed by contact.
Bending shear deformation
Figure 982905DEST_PATH_IMAGE016
Is calculated as follows:
Figure 875775DEST_PATH_IMAGE017
in the formula,
Figure 118537DEST_PATH_IMAGE009
is a normal load;
e is the comprehensive elastic modulus;
b is the tooth width;
Figure 514883DEST_PATH_IMAGE018
the angle of engagement being the point of action;
Figure 184899DEST_PATH_IMAGE019
the distance from the action point of the meshing force to the fixed part of the root circle;
and x and y are coordinates of left and right points of the gear tooth meshing normal force respectively.
Deformation of gear tooth base
Figure 299486DEST_PATH_IMAGE020
Is calculated as follows:
Figure 844474DEST_PATH_IMAGE021
in the formula,
Figure 360906DEST_PATH_IMAGE009
is a normal load;
e is the comprehensive elastic modulus;
b is the tooth width;
Figure 201823DEST_PATH_IMAGE018
the angle of engagement being the point of action;
Figure 803706DEST_PATH_IMAGE019
the distance from the action point of the meshing force to the fixed part of the root circle;
Figure 653850DEST_PATH_IMAGE022
the tooth thickness at the tooth root.
Deformation by contact
Figure 24789DEST_PATH_IMAGE015
Is calculated as follows:
Figure 302186DEST_PATH_IMAGE023
in the formula,
Figure 627251DEST_PATH_IMAGE009
is a normal load;
e is the comprehensive elastic modulus;
b is the tooth width;
Figure 15507DEST_PATH_IMAGE024
the tooth thickness of the contact point of the gear 1;
Figure 506531DEST_PATH_IMAGE025
the tooth thickness of the contact point of the gear 2;
c is calculated as follows:
Figure 689251DEST_PATH_IMAGE026
，
in the formula,
Figure 265725DEST_PATH_IMAGE009
is a normal load;
e is the comprehensive elastic modulus;
b is the tooth width;
Figure 192093DEST_PATH_IMAGE027
is the curvature radius of the tooth surface contact point of the gear 1;
Figure 537624DEST_PATH_IMAGE028
is the radius of curvature at the point of tooth surface contact of the gear 2.
Radius of curvature at point of tooth flank contact
Figure 672937DEST_PATH_IMAGE029
Is calculated as follows:
Figure 471129DEST_PATH_IMAGE030
in the formula,
Figure 466767DEST_PATH_IMAGE031
is the diameter of the base circle of the gear,
Figure 401225DEST_PATH_IMAGE032
is the contact point diameter of the gear.
Base diameter of gear
Figure 191326DEST_PATH_IMAGE031
The calculation formula of (a) is as follows:
Figure 742393DEST_PATH_IMAGE033
in the formula,
m is a gear module;
Figure 10564DEST_PATH_IMAGE034
the number of teeth of the gear;
Figure 566572DEST_PATH_IMAGE035
is the gear pressure angle.
Contact point diameter of gear 1
Figure 793154DEST_PATH_IMAGE036
Is calculated as follows:
Figure 300359DEST_PATH_IMAGE037
in the formula,
Figure 637799DEST_PATH_IMAGE038
the base circle diameter of the gear 1;
Figure 812429DEST_PATH_IMAGE039
is the addendum circle diameter of the gear 1;
Figure 678753DEST_PATH_IMAGE040
for the length of the meshing line to be,
Figure 702948DEST_PATH_IMAGE041
is a contact line parameter.
Contact point diameter of gear 2
Figure 312921DEST_PATH_IMAGE042
Is calculated as follows:
Figure 342057DEST_PATH_IMAGE043
in the formula,
Figure 644862DEST_PATH_IMAGE044
the base circle diameter of the gear 2;
Figure 392238DEST_PATH_IMAGE045
is the addendum circle diameter of the gear 2;
Figure 71481DEST_PATH_IMAGE040
is the length of the meshing line;
Figure 955124DEST_PATH_IMAGE041
is a contact line parameter.
Diameter of addendum circle
Figure 930295DEST_PATH_IMAGE046
Is calculated as follows:
Figure 899388DEST_PATH_IMAGE047
in the formula,
m is a gear module;
z is the number of gear teeth;
Figure 116743DEST_PATH_IMAGE048
the tooth crest height coefficient;
Figure 120471DEST_PATH_IMAGE003
is the coefficient of variation.
Length of meshing line
Figure 765079DEST_PATH_IMAGE040
Is calculated as follows:
Figure 221468DEST_PATH_IMAGE049
in the formula,
Figure 976934DEST_PATH_IMAGE039
is the tooth tip of the gear 1Diameter of the circle;
Figure 339564DEST_PATH_IMAGE038
is the base circle diameter of the gear 1;
Figure 420652DEST_PATH_IMAGE045
is the addendum circle diameter of the gear 2;
Figure 364337DEST_PATH_IMAGE044
is the base circle diameter of the gear 2;
a is a center distance;
Figure 657915DEST_PATH_IMAGE050
is a pitch circle pressure angle.
Pitch circle pressure angle
Figure 370656DEST_PATH_IMAGE050
Is calculated as follows:
Figure 622646DEST_PATH_IMAGE051
in the formula,
Figure 53628DEST_PATH_IMAGE052
the number of teeth of gear 1;
Figure 652361DEST_PATH_IMAGE053
the number of teeth of the gear 2;
m is a gear module;
Figure 219609DEST_PATH_IMAGE035
is the gear pressure angle;
a is the center distance.
S2: according to the time obtained by the calculation in the step oneVariable mesh stiffness
Figure 376921DEST_PATH_IMAGE001
Calculating the gear engagement exciting force generated by the gear according to the Newton formula
Figure 295198DEST_PATH_IMAGE002
。
Gear mesh exciting force
Figure 196158DEST_PATH_IMAGE002
Is calculated as follows:
Figure 883491DEST_PATH_IMAGE054
in the formula,
TE is a gear transmission error;
Figure 211705DEST_PATH_IMAGE001
is a time varying meshing stiffness.
The gear transfer error TE is calculated as follows:
Figure 115813DEST_PATH_IMAGE055
，
in the formula,
Figure 820464DEST_PATH_IMAGE056
is the base radius of the driven gear;
Figure 362304DEST_PATH_IMAGE057
is the rotation angle of the driven gear;
Figure 126998DEST_PATH_IMAGE058
the radius of the base circle of the driving gear;
Figure 754288DEST_PATH_IMAGE059
is the angle of the driving gear.
S3: and establishing a finite element analysis model of the gearbox shell, applying the exciting force calculated in the step S2 to the shell, and calculating the vibration response of the surface of the shell.
Specifically, an exciting force is applied to a bearing seat of the housing.
Taking a single degree of freedom vibration system as an example, the vibration differential equation of the vibration response is as follows:
Figure 997051DEST_PATH_IMAGE060
the solution to this equation is assumed to be of the following form:
Figure 658976DEST_PATH_IMAGE061
in the formula,
Figure 830457DEST_PATH_IMAGE062
and a is the excitation frequency and the response amplitude of the system, respectively.
Will be provided with
Figure 210622DEST_PATH_IMAGE063
Substituting into a vibration differential equation of the vibration response to obtain:
Figure 991497DEST_PATH_IMAGE064
in the formula,
Figure 773508DEST_PATH_IMAGE065
the natural frequency of the system under the condition of no damping;
Figure 825210DEST_PATH_IMAGE066
Figure 692672DEST_PATH_IMAGE067
is the damping ratio, defined as the damping c of the system to the critical damping ratio
Figure 542816DEST_PATH_IMAGE068
In a ratio of
Figure 680798DEST_PATH_IMAGE069
Critical damping
Figure 958196DEST_PATH_IMAGE068
The definition is as follows:
Figure 47375DEST_PATH_IMAGE070
the solution to the equation is:
Figure 435631DEST_PATH_IMAGE071
when in use
Figure 661076DEST_PATH_IMAGE067
The system will vibrate when < 1, and the response of the system or the solution of the equation is
Figure 843795DEST_PATH_IMAGE072
S4: and extracting the surface mesh of the shell finite element model in the step S3, and mapping the shell vibration response to the surface mesh of the shell, thereby calculating the radiation noise y at the sound pressure level of one meter according to the direct boundary element method.
For example, using the vibration velocity data mapping diagram shown in fig. 3, the shell vibration velocity is mapped onto the shell surface grid, and the velocity of node a on the target grid is calculated as follows:
Figure 184385DEST_PATH_IMAGE073
non-boundary elements in sound field V
Figure 110752DEST_PATH_IMAGE074
Sound pressure at any point r on
Figure 456283DEST_PATH_IMAGE075
：
Figure 75483DEST_PATH_IMAGE076
In the formula:
coefficient matrix vector
Figure 873675DEST_PATH_IMAGE077
And
Figure 338154DEST_PATH_IMAGE078
respectively as follows:
Figure 803771DEST_PATH_IMAGE079
；
Figure 95337DEST_PATH_IMAGE080
；
Figure 115246DEST_PATH_IMAGE081
and
Figure 914574DEST_PATH_IMAGE082
is a boundary
Figure 969118DEST_PATH_IMAGE074
Each unit of
Figure 664542DEST_PATH_IMAGE083
At any point insideSound pressure and normal velocity, the values of which are calculated by the following equations:
Figure 702905DEST_PATH_IMAGE084
；
Figure 774766DEST_PATH_IMAGE085
；
wherein,
Figure 453790DEST_PATH_IMAGE086
is a shape function of the cell;
Figure 585694DEST_PATH_IMAGE087
is a certain unit
Figure 580195DEST_PATH_IMAGE083
Number of nodes above.
Unit shape function
Figure 721326DEST_PATH_IMAGE086
1 at node i and a unit shape function at the other nodes of the unit
Figure 750462DEST_PATH_IMAGE086
Assembled into global shape functions
Figure 53267DEST_PATH_IMAGE088
Whole boundary element grid
Figure 800644DEST_PATH_IMAGE074
On the upper part
Figure 715772DEST_PATH_IMAGE089
Figure 864994DEST_PATH_IMAGE090
Wherein:
Figure 73121DEST_PATH_IMAGE091
the number of nodes for all the border metagrids.
The vibrational response of the housing may be not only velocity but also displacement or acceleration. The method of mapping displacements or accelerations onto the shell surface grid is prior art and will not be described in detail here.
S5: and (3) constructing a relation between the gear variable and the radiation noise at the sound pressure level of one meter, namely, a first-order response surface model taking the gear parameter variable as an input variable and the radiation noise y at the sound pressure level of one meter as an output.
The method comprises the following steps:
s51: determining gear parameter variables and tolerance ranges;
s52: determining a plurality of groups of gear parameter variable values according to the gear parameter variable and the tolerance range;
s53: executing the steps S1 to S4, and calculating the response value of the gear one-meter sound pressure level radiation noise corresponding to each group of gear parameter variable values;
and S54, obtaining the relation between the input variable and the output variable by utilizing the variable value of each group of gear parameters and the response value of the gear one-meter sound pressure level radiation noise corresponding to the variable value of each group of gear parameters.
Specifically, the method comprises the following steps:
first, gear parameter variables and tolerances are determined, as shown in table 1.
TABLE 1 design variables and tolerances
Variables of Number of teeth z Modulus m Coefficient of variation
Figure 42214DEST_PATH_IMAGE003
 Width of tooth b
Mean value 91 1.41 0.1753 19
Tolerance of ±5 ±0.3 ±0.1 ±2
Then, a specific sample point is selected.
As shown in table 2, 29 sets of sample points were selected; in practice, the number of groups of selected sample points can be adjusted according to the tolerance range.
TABLE 2 response surface test design sample points and response values of radiated noise
Figure 259569DEST_PATH_IMAGE092
Figure 263297DEST_PATH_IMAGE093
Based on the sample points in table 2, 29 response values of the gear radiation noise at sound pressure level of one meter are obtained through 29 calculations from step S1 to step S4, and are listed in the last column of table 2.
Fitting the sample points of table 2 with a quadratic polynomial using a response surface method to obtain the relationship between the input variable and the output variable:
Figure 907905DEST_PATH_IMAGE094
s6: according to the first-order response surface model in step S5, the variable tooth number, modulus, displacement coefficient, and tooth width are optimized using a genetic algorithm with the one-meter sound pressure level radiation noise y being the lowest.
The foregoing shows and describes the general principles, essential features, and advantages of the invention. It will be understood by those skilled in the art that the present invention is not limited to the embodiments described above, which are described in the specification and illustrated only to illustrate the principle of the present invention, but that various changes and modifications may be made therein without departing from the spirit and scope of the present invention, which fall within the scope of the invention as claimed. The scope of the invention is defined by the appended claims and equivalents thereof.

Claims (6)

1. A gear noise radiation rapid optimization method based on a response surface method is characterized in that: the method comprises the following steps:
s1: determining gear parameter variables, and calculating the time-varying meshing stiffness of the gear set by using the gear parameter variables
Figure 811940DEST_PATH_IMAGE001
；
S2: time-varying meshing stiffness according to step S1
Figure 841076DEST_PATH_IMAGE001
Calculating gear mesh excitation force generated by gear
Figure 645347DEST_PATH_IMAGE002
；
S3: establishing a finite element analysis model of the gearbox shell, and calculating the gear engagement exciting force obtained in the step S2
Figure 127143DEST_PATH_IMAGE002
Applying the vibration response to the shell, and calculating the vibration response of the surface of the shell;
s4: extracting the surface mesh of the shell finite element model in the step S3, and mapping the shell vibration response to the surface mesh of the shell, thereby calculating the radiation noise y at the sound pressure level of one meter according to the direct boundary element method;
s5: constructing a first-order response surface model with a gear parameter variable as an input variable and a one-meter sound pressure level radiation noise y as an output;
s6: and optimizing the gear parameter variables according to the first-order response surface model in the step S5.
2. The method for rapidly optimizing the gear noise radiation based on the response surface method as claimed in claim 1, wherein: in step S1, calculating the time-varying meshing stiffness of the gear set according to the Weber-Banaschek gear stiffness calculation method
Figure 540807DEST_PATH_IMAGE001
。
3. The method for rapidly optimizing the gear noise radiation based on the response surface method as claimed in claim 1, wherein: in step S1, the gear parameter variables include the number of teeth z, the modulus m, and the shift coefficient
Figure 690029DEST_PATH_IMAGE003
And a tooth width b.
4. The method for rapidly optimizing the gear noise radiation based on the response surface method as claimed in claim 1, wherein: in step S3, the gears are engaged with exciting force
Figure 163736DEST_PATH_IMAGE002
Applied to the housing bearing seats.
5. The method for rapidly optimizing the gear noise radiation based on the response surface method as claimed in claim 1, wherein: in step S5, the method includes the steps of:
s51: determining gear parameter variables and tolerance ranges;
s52: determining a plurality of groups of gear parameter variable values according to the gear parameter variable and the tolerance range;
s53: executing the steps S1 to S4, and calculating the response value of the gear one-meter sound pressure level radiation noise corresponding to each group of gear parameter variable values;
s54: and obtaining the relation between the input variable and the output variable by utilizing the variable value of each group of gear parameters and the response value of the gear one-meter sound pressure level radiation noise corresponding to the variable value of each group of gear parameters.
6. The method for rapidly optimizing the gear noise radiation based on the response surface method as claimed in claim 1, wherein: in step S6, the variable tooth number, modulus, displacement coefficient, and tooth width are optimized using a genetic algorithm with the lowest radiation noise y at a sound pressure level of one meter as a target.
CN202110764678.7A 2021-07-07 2021-07-07 Rapid optimization method of gear noise radiation based on response surface method Active CN113255084B (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN202110764678.7A CN113255084B (en) 2021-07-07 2021-07-07 Rapid optimization method of gear noise radiation based on response surface method

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN202110764678.7A CN113255084B (en) 2021-07-07 2021-07-07 Rapid optimization method of gear noise radiation based on response surface method

Publications (2)

Publication Number Publication Date
CN113255084A true CN113255084A (en) 2021-08-13
CN113255084B CN113255084B (en) 2022-05-06

Family

ID=77190819

Family Applications (1)

Application Number Title Priority Date Filing Date
CN202110764678.7A Active CN113255084B (en) 2021-07-07 2021-07-07 Rapid optimization method of gear noise radiation based on response surface method

Country Status (1)

Country Link
CN (1) CN113255084B (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN116992604A (en) * 2023-09-28 2023-11-03 盛瑞传动股份有限公司 Method, device, equipment and medium for optimizing structure parameters of connecting disc

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102314534A (en) * 2011-06-03 2012-01-11 东北大学 Gear profile modification method based on vibration reliability and genetic algorithm
CN103971006A (en) * 2014-05-16 2014-08-06 清华大学 Calculation method for driving axle gear dynamic characteristics considering main speed reducer housing
CN103982635A (en) * 2014-06-11 2014-08-13 北京化工大学 Composite damping device for vibration and noise reduction of gear shafting
CN105138734A (en) * 2015-07-31 2015-12-09 吉林大学 Improved method for optimally designing noise of main parameter of bevel gear of transmission
CN107391816A (en) * 2017-07-04 2017-11-24 清华大学 A kind of Drive axle housing vibration noise numerical value determines method
CN110362858A (en) * 2019-06-05 2019-10-22 徐州圣邦机械有限公司 A kind of reliability estimation method of high pressure crescent gear pump gear pair
CN111651846A (en) * 2020-06-02 2020-09-11 四川长虹空调有限公司 Automatic optimization method for pipeline design of refrigeration equipment

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102314534A (en) * 2011-06-03 2012-01-11 东北大学 Gear profile modification method based on vibration reliability and genetic algorithm
CN103971006A (en) * 2014-05-16 2014-08-06 清华大学 Calculation method for driving axle gear dynamic characteristics considering main speed reducer housing
CN103982635A (en) * 2014-06-11 2014-08-13 北京化工大学 Composite damping device for vibration and noise reduction of gear shafting
CN105138734A (en) * 2015-07-31 2015-12-09 吉林大学 Improved method for optimally designing noise of main parameter of bevel gear of transmission
CN107391816A (en) * 2017-07-04 2017-11-24 清华大学 A kind of Drive axle housing vibration noise numerical value determines method
CN110362858A (en) * 2019-06-05 2019-10-22 徐州圣邦机械有限公司 A kind of reliability estimation method of high pressure crescent gear pump gear pair
CN111651846A (en) * 2020-06-02 2020-09-11 四川长虹空调有限公司 Automatic optimization method for pipeline design of refrigeration equipment

Non-Patent Citations (3)

* Cited by examiner, † Cited by third party
Title
SHENGNAN WANG，等: "An Improved Computational Method for Vibration Response and Radiation Noise Analysis of Two-Stage Gearbox", 《IEEE ACCESS》 *
张在强: "电动汽车减速器壳体辐射噪声研究", 《中国优秀硕士学位论文全文数据库 工程科技Ⅱ辑》 *
李小彭,等: "含齿面分形啮合刚度的齿轮传动系统动力学", 《哈尔滨工业大学学报》 *

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN116992604A (en) * 2023-09-28 2023-11-03 盛瑞传动股份有限公司 Method, device, equipment and medium for optimizing structure parameters of connecting disc
CN116992604B (en) * 2023-09-28 2024-01-02 盛瑞传动股份有限公司 Method, device, equipment and medium for optimizing structure parameters of connecting disc

Also Published As

Publication number Publication date
CN113255084B (en) 2022-05-06

Similar Documents

Publication Publication Date Title
Özgüven et al. Dynamic analysis of high speed gears by using loaded static transmission error
CN103615501B (en) A kind of small harmonic reducer and Optimization Design thereof
CN113255084B (en) Rapid optimization method of gear noise radiation based on response surface method
CN102314534A (en) Gear profile modification method based on vibration reliability and genetic algorithm
CN107391816A (en) A kind of Drive axle housing vibration noise numerical value determines method
CN109190227A (en) Based on the complicated tooth base Meshing Stiffness of Spur Gears calculation method of parsing-finite element
CN110222471B (en) Full-coupling dynamics modeling method for gear transmission system
CN113051681B (en) Gear pair meshing rigidity calculation method and terminal equipment
Wang et al. A model to determine mesh characteristics in a gear pair with tooth profile error
CN108416120A (en) A kind of determination method of straight spur gear double-teeth toothing region weight-distribution factor
CN111079300B (en) Straight gear meshing rigidity calculation method considering tooth direction error
CN108519224B (en) A method of verifying two-stage fixed axis gear transmission system vibration coupling feature
CN114117849A (en) Blade shroud damping vibration attenuation analysis method of low-pressure turbine blade/disk rotor
CN110688614B (en) Multi-tooth meshing composite stress solving method for cup-shaped flexible wheel of harmonic reducer
CN114201888A (en) Loss and efficiency simulation calculation method of planetary gear train
CN116861585A (en) Optimized design method for vibration response of spur gear
Zhang et al. Contact Mechanics Analysis and Optimization of Shape Modification of Electric Vehicle Gearbox.
CN108846189A (en) A kind of gear pair meshing characteristic analysis method
CN113465915A (en) Gear box gear fault degree determination method based on vibration transmission
CN116432440A (en) Gear dynamics analysis method considering uncertainty of modification parameters
Wink et al. Investigation of tooth contact deviations from the plane of action and their effects on gear transmission error
CN113656960B (en) Method for analyzing nonlinear vibration of gear of speed reducer, computer equipment and storage medium
CN110866316B (en) Speed reducer bonding diagram model optimization method based on six-degree-of-freedom gear meshing model
CN112507485A (en) Bevel gear time-varying meshing stiffness analysis method based on slice coupling theory
Westphal et al. Design of Tooth Flank Modifications in Transmission Systems Considering Dynamic Misalignments

Legal Events

Date Code Title Description
PB01 Publication
PB01 Publication
SE01 Entry into force of request for substantive examination
SE01 Entry into force of request for substantive examination
GR01 Patent grant
GR01 Patent grant