nvh、动力学轮胎技术管理商业模式及其他主题-ht1整车

Contents1Background研究背景2Global

and

Direct

Transmissibilities

Method全局-直接传递率矩阵方法3Numerical

Case

Studies数值案例分析4ysisAuto-body

Vibration车身振动分析应用5Conclusion结论1.

Background研究背景The

NVH

performance

of

automobile

has

been

paid

close

attention

to

by

customers

and

automobile

manufacturers汽车的NVH性能受到顾客及汽车厂商的广泛关注和重视Automotive

NVH

performance

汽车NVH性能空气噪声结构噪声150100001000Frequency

(Hz)ResponseEngine

excitationPage

3Road

excitationWind

excitation1.

Background研究背景Structural

Vibration

and

Noise

Transmission

结构振动噪声传递过程

F

i

P

jPPjFi源通道源接受体源源源源源

P

通道通道

P

激励源（source）传递路径（path）接受结构（receiver）Classical

Transfer

Pathysis

(TPA)经典传递路径分析方法:-

Direct

measurement

method直接测量法Complex

stiffness

method复刚度法Inverse

matrix

method逆矩阵法The

classic

TPA

has e

the

standardTPA

in

the

automotive

industry经典TPA已成为汽车行业的标准TPAPage

41.

Background研究背景Transfer

Pathysis

传递路径分析TPAClassicalTPAOPAXOperationalTPAGTDTComponentTPAFATGTDT方法的特点和优点：No

force

determination不需要测量工况力No

disassembly不需要拆分系统yzing

the

response

transmissionamongsubsystems分析响应在子系统之间的传递Potential

response

predictivefunction潜在的响应

功能；AbsoluteTPA

and

Relative

TPA

methods绝对传递路径分析方法和相对传递路径分析方法Page

5ContentsBackground研究背景2Global

and

Direct

Transmissibilities

Method全局-直接传递率矩阵方法3Numerical

Case

Studies数值案例分析4ysisAuto-body

Vibration车身振动分析应用5Conclusion结论12.

Global

and

Direct

Transmissibilities

Method全局-直接传递率矩阵方法Basic

GTDT

Theory

全局-直接传递率矩阵方法ii

1i

1js1niiT

Dii

TG

1ijijijjjTG

X

X

=

H

Hiij

jii

iN

1j

1,

j

i

T

D

X

extX

T

D

Xijii1T

DT

D1ij

TG

n

DOF

discrete

systemn

度离散系统ext

GX

=

T

1X

Xop

=TD

ΛD

Xop

ΛD

Xop,extii

1i

1js1nj

jjPage

7j

ij

ij

jjXˆ

op,ext

TGp

X

op,ext

TˆG

TGp

TGpXˆ

op

=TˆD

Λˆ

D

Xˆop

Λˆ

D

Xˆ

op,extPath

disconnecting

system路径断开系统2.

Global

and

Direct

Transmissibilities

Method全局-直接传递率矩阵方法ii

1i

1js1nn

DOF

discrete

systemn

度离散系统11ˆ

ˆˆ

ˆ

ˆˆGnn1

Hii

1

H

jj

1

HT

Hdiag

1

Hii

1i

1js1nPath

disconnecting

system路径断开系统11nnTG

Hdiag1

H

1

Hn1ninjZ

jiZ

ZZZ1n

Z11

Zi1Zin

ZiiZ1i

Z1

j

Zij

0Z

j1Z

jn

0

Z

jjZnn

Zˆ

Zˆ

Hˆ

1Page

8New

dynamic

stiffness

matrix新系统动刚度矩阵Basic

GTDT

Theory

全局-直接传递率矩阵方法2.

Global

and

Direct

Transmissibilities

Method全局-直接传递率矩阵方法11iijjnn1

HˆTˆ

G

Hˆ

diag1

Hˆii

1i

1js1nPath

disconnecting

system路径断开系统1G

T

diag

HH

Z11nnsjsjTG

1

T

GvT

Gv

H

Zsj

ss

sj11001i1

j1ni1inGpj1jnn1nnTGvTGvTGv

TGvni

njTGvTGv

TGvTGv

TGv

TGvii

ij1

TGvTGv

TGv

TGvji

jjTGvTGv

T11iijjnnTGp

Hˆ

diag1

H

1

H

1

H

1

H1

Hˆ

1

HˆPage

9Transformation

matrix转换矩阵Basic

GTDT

Theory

全局-直接传递率矩阵方法Page102.

Global

and

Direct

Transmissibilities

Method全局-直接传递率矩阵方法jjT

Gp

Hˆ

Hsj

sjsjsjjjHˆTˆG

HˆTˆG

TGp

TGpsj

sj

jjXˆ

ext

T

Gp

X

extj

jj

j11iijjnnH

H

Hop,extX

TG

Xop

diagH1Fop11iijjnnHˆ

Hˆ

HˆXˆop,ext

diag

HˆFopTGXopTGpTˆ

DXˆ

op

devTˆD

Xˆop

Λˆ

D

Xˆ

op,extXop,extTˆ

GXˆop,extXˆ

opResponsepredictionprocess响应

流程Basic

GTDT

Theory

全局-直接传递率矩阵方法Contents1Background研究背景2Global

and

Direct

Transmissibilities

Method全局-直接传递率矩阵方法3Numerical

Case

Studies数值案例分析4Auto-body

Vibration车身振动分析应用ysis5Conclusion结论3.

Numerical

Case

Studies数值案例分析Nine

DOFs

Discrete

System

九就

度系统M9K89C89

K69C69

K59C59K78C35C78

K46C46

K35C23K24C24

K23K17C17K12C12K01C01M8M

7M

6M5M

4M

3M

2M1Parameters单元参数质量单元M(kg)M1=2.0,

M2=1.0,M3=5.5,M4=3.0,M5=6.0,

M6=8.0,

M7=2.5,

M8=3.5,M9=4.0弹性单元K(kg/mm)K01=0.1,

K02=0.4,

K17=0.5,

K23=0.35,

K24=0.15,

K35=0.13,

K46=0.6,

K58=0.27,

K68=0.39,

K78=0.48,

K89=0.29阻尼单元C(kg/s)C01=1.1,

C12=3.6,

C17=6.2,

C23=4.5,

C24=9.0,

C35=8.3,C46=11.3,

C58=14,

C68=16.3,

C78=5.2,

C89=7.0Setup系统设置:Force

applied

on

mass

5,7,8

and

9工况力：施加在质量块5、7、8和9Key

subsystems：1,

2,

3

and

4关键子系统：1、2、3和4ysis分析设置：Remove

the

link

between

mass

2

and3去掉质量块2和3之间的连接GTDT

implementation

steps实施步骤：Step

1

Measure

the

global

transmissibilitymatrix

of

the

original

system步骤1

测量原系统全局传递率矩阵Step

2

Measure

operational

responses

ofmass

1,

2,

3

and

4步骤2

测量工况下1、2、3和4的响应Step

3

Predict

new

system

responses

using

GTDT步骤

3

用GTDT技术

新系统响应Page

123.

Numerical

Case

Studies数值案例分析Nine

DOFs

Discrete

System

九就

度系统New

displacement

of

mass

1质量块1的新位移New

displacement

of

mass

2质量块2的新位移New

displacement

of

mass

3质量块3的新位移New

displacement

of

mass

4质量块4的新位移11TˆG12TˆG11Tˆ

D12Tˆ

DPage

133.

Numerical

Case

Studies数值案例分析FEM ysis

有限元分析FoABc1tc2

c3xyzxyz断开连接点disconnectingVibration

transmission

system振动传递系统Path

disconnectingsystem传递路径断开系统1325F4xyzFEM

model有限元模型Page

143.

Numerical

Case

Studies数值案例分析FEM ysis

有限元分析动刚度Link

1Link

2Link

3Link

4

连接点

1

连接点

2

连接点

3

连接点

4

Dynamic

X0.1520.1660.1500.113stiffnessY0.2070.2300.2120.145(kN

mm-1)Z0.1500.1200.1530.070Rubber

parameters悬置刚度参数xxxyyzxzyyzyy1z

2z

3x

4xyzBottom

pointsTop

pointszx

yzxysis分析设置：Remove

the

link

between

mass

2

and

3去掉质连接点2和3之间的连接Setup系统设置:Force

applied

on

the

top

plate工况力：施加在上板Key

subsystems：1,

2,

3,

4

and

5关键子系统：1、2、3、4和5response

with

1

ZTRemoved1

ZT断开后目标响应response

with

2

ZTRemoved2

ZT断开后目标响应response

with

3

ZTRemovedresponse

with

4

ZTRemoved3

ZT断开后目标响应4

ZT断开后目标响应Page15Contents1Background研究背景2Global

and

Direct

Transmissibilities

Method全局-直接传递率矩阵方法3Numerical

Case

Studies数值案例分析4ysisAuto-body

Vibration车身振动分析应用5Conclusion结论4.

Auto-body

Vibration车身振动应用分析ysisFEM

of

a

car

轿车有限元模型Finite

element

model

of

apassenger

car车身有限元分析模型质量(kg)质心局部坐标(mm)转动惯量(kgm2)XCYCZCIm

xxIm

yyIm

zz157.096.0-49.3-256.113.053.807.80Parameters

of

the

power

plant动力总成惯性参数123xyz3条路径座椅安装点加速度3条路径3条路径FAcceleration

level

at

the

seatmounting

point座椅安装点加速度响应谱Key

frequencypoint关键频率点137、147

and176HzPage

174.

Auto-body

Vibration车身振动应用分析ysisRelative

TPA

相对传递路径分析模型座椅安装点加速度xyz

xy

zxyz发一侧车身一侧xxy

z悬置1悬置2悬置3发一侧座椅安装点加速度xxy

z

x

x

y

zxyzxy

yz

z车身一侧悬置1悬置2悬置3The

classical

TPA

model经典传递路径分析模型The

Relative

TPA

model相对传递路径分析模型Page

184.

Auto-body

Vibration车身振动应用分析ysisResults

分析结果The

seat

mounting

pointacceleration

with

zero

dynamicstiffness

of

the

mount动刚度设为0的座椅安装点加速度No.悬置Direction方向137Hz147Hz176Hz1x-x0.24751.22410.2727y-y-1.8231-0.05380.0993z-z7.21171.0375-9.66912x-x-0.65600.3007-0.0994y-y-0.05330.1811-0.1900z-z0.22500.5857-23.19223x-x-0.67480.51827.6701y-y0.6790-0.20860.3096z-z-8.2858-10.6365-5.6692Path

order传递路径排序Relative

TPA相对TPAClassical

TPA经典TPA11

x-x3

z-z21

z-z2

y-y32

z-z2

z-z43x-x1

z-z52x-x3

y-y62

y-y2

x-x71

y-y1

y-y83

y-y1

x-x93

z-z3x-xTransfer

path

importanceranking

order

in

147

Hz147Hz下传递路径重要性排序Insertion

loss

values损失值2ref Di,

j

ii,

jX2X

X

2

X

2IL

10

log10

log

ref

Page

19Contents1Background研究背景2Global

and

Direct

Transmissibilities

Method全局-直接传递率矩阵方法3Numerical

Case

Studies数值案例分析4ysisAuto-body

Vibration车身振动分析应用5Conclusion结论Page

215.

Conclusion结论The

GTDT

prediction

technique

proposed

in

this

p

r

proved

to be

an

efficient