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A study on the reduction of structure-borne noise in

hydraulic power unit with elastic mounting

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본 논문을 박성용의 공학석사 학위논문으로 인준함.

년

월

일

2017

07

03

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List of Tables ··· iv List of Figures ··· vi Abstract ··· vii 1. ··· 1 1.1 ··· 1 1.2 ··· 2 2. ··· 3 2.1 ··· 3 2.2 ··· 5 2.3 ··· 12 2.4 ··· 14 3. ··· 19 3.1 ··· 19 3.2 ··· 24 3.3 ··· 26 3.4 1 ··· 37 3.5 2 ··· 48 3.6 ··· 55 4. ··· 56 4.1 ··· 56 4.2 ··· 59

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5. ··· 63

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List of Tables

Table 1 Classification of equipment ··· 4

Table 2 Specification of acceleration measurement device ··· 6

Table 3 Specification of hydraulic power unit ··· 8

Table 4 Measurement result of major frequencies ··· 18

Table 5 Material property ··· 24

Table 6 Natural frequency of spring-mass model ··· 25

Table 7 Comparison of major frequency(Initial model) ··· 27

Table 8 Result of modal frequency(Frist reinforcement model) ··· 38

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List of Figures

Fig. 1 Avenue of path of underwater radiation noise ··· 2

Fig. 2 Test criteria of structure-borne noise ··· 4

Fig. 3 Test criteria of vibration measurement test ··· 5

Fig. 4 Nine measuring positions ··· 6

Fig. 5 Installation of hydraulic power unit ··· 7

Fig. 6 Measurement result of structure-borne noise(1/3 octave band) ·· 12

Fig. 7 Measurement result of motor bearing housing ··· 13

Fig. 8 Measuring position of motor bearing housing ··· 13

Fig. 9 Measurement result of structure-borne noise(narrow band) ··· 17

Fig. 10 FE modeling and mesh(Initial model) ··· 26

Fig. 11 Mode shape of modal analysis(Initial model) ··· 30

Fig. 12 Result of harmonic analysis(Initial model) ··· 33

Fig. 13 Total deformation by harmonic analysis(Initial model) ··· 36

Fig. 14 FE modeling and mesh(Frist reinforcement model) ··· 37

Fig. 15 Result of harmonic analysis(Frist reinforcement model) ··· 42

Fig. 16 Total deformation by harmonic analysis(Frist reinforcement model) ···· 47

Fig. 17 FE modeling and mesh(Second reinforcement model) ··· 48

Fig. 18 Result of harmonic analysis(Second reinforcement model) ··· 52

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Fig. 21 Measurement result of structure-borne noise(1/3 octave band) ·· 59 Fig. 22 Measurement result of structure-borne noise(narrow band) ··· 62

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A study on the reduction of structure-borne noise in

hydraulic power unit with elastic mounting

Park, Sung Yong

Department of Mechanical Systems Engineering

Graduate School of Korea Maritime and Ocean University

Abstract

In the case of the naval vessel equipment, air-borne noise and structure-borne noise generated from the equipment are ultimately transmitted to the hull, propagated in the water, and the possibility of being exposed to the enemy is increased, and the survival of the naval

vessel is also directly connected. These air-borne noise and

structure-borne noise are also very important factors from the

viewpoint of crew members' comfort. Air-borne noise and

structure-borne noise are strictly managed based on the standards of the US Navy, and the requirement for low vibration and noise is recognized as basic quality that equipment for a naval vessel must have, and research and improvements are being made.

In this study, the cause of excessive vibration due to the rotational motion of the motor and the reciprocating motion of the hydraulic pump in the hydraulic power unit was analyzed through the structure-borne

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KEY WORDS : Structure-borne noise ; Air-borne noise

; Hydraulic power unit , naval vessel equipment

, Reduction .

noise test.

The study on the reduction of the structure-borne noise of the hydraulic power unit through the design change of the hydraulic tank was examined.

Modal analysis was performed by generating a finite element model of a hydraulic tank for frequency avoidance that exhibited a high acceleration level in the structure-borne noise evaluation and harmonic analysis was

performed to verify the validity of the structure-borne noise.

Verification of the improved shape was confirmed by confirming that the acceleration level of the frequency was reduced.

Finally, it is confirmed that the finite element analysis is effective to

reduce the structure-borne noise in the final test evaluation by

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1

1.1

. . Fig. 1 , . , .[1] , . , , / .[2] . , , , , , , , .

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1.2

. . , , , , . , , . , , .[4] , .

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2

2.1

MIL-STD-740-1(SH), MIL-STD-740-2(SH) . . ( ) . MIL-STD-167-1A:2005(Type II) , . 2.1.1 (MIL-STD-740-2(SH):1986)

Table 1 Type I~IV , Type II 5 dB . Fig. 2 1/3 10 Hz 10000 Hz . 11 Hz 1/4 . , . . . 15 dB .[3]

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Type Equipment

Type I Compressor, internal combustion engines Type II Pump, valve, life support equipment Type III Other than type I & 2

Type IV Vane-axial fan

Table 1 Classification of equipment

Fig. 2 Test criteria of structure-borne noise

2.1.2 (MIL-STD-167-1A:2005)

, , ,

. 1 Hz 1 Hz 1000 Hz , Fig. 3 (Displacement single amplitude) , .

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Fig. 3 Test criteria of vibration measurement test

2.2

Type II 5 dB Fig. 2 . Fig. 4 , Fig. 5 . 2.2.1 1/3 Octave band 10 Hz 10000 Hz , Narrow band 1 Hz 750 Hz , Hanning 1 Hz . Table 2 .

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Item Device name Signal analyzer OROS_OR36

Accelerometer MMF_KS943B100 KS-77C-10 Vibration Calibrator PCB_394C06

Frequency Span 1/3 octave band 10 Hz ~ 10000 Hz Narrow band 1 Hz ~ 750 Hz Window function Hanning window

Resolution 750 line Averaging 30 times

Table 2 Specification of acceleration measurement device

2.2.2

Fig. 4 ,

9 , 24

MPa(240 bar), 1170 rpm Table 3 .

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(a) Photo of hydraulic power unit

(b) Measuring position (c) Pressure meter

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2.2.3 . 1170 rpm , _ 19.5 Hz . _    (1) 9 _ 175.5 Hz . _   ×   (2)

Table 3 Specifications of hydraulic power unit

1. Model Hydraulic power unit

2. Size (W) 1500 mm × (L) 1130 mm × (H) 1866 mm 3. Mass 1400 kg

4. Supply AC 440 V, 60 Hz, 3 P 5. Working pressure 24 MPa (240 bar)

6. Motor

Revolutions : 1170 rpm Power : 45 kW

Mass : 450 kg

7. Pump

Type : piston pump

Installed number of piston : 9 EA Revolutions : 1170 rpm

Mass : 31.8 kg 8. Mount Installed number : 9 EA

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2.2.4 , 1 9 . (a) Point 1 (b) Point 2

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(c) Point 3

(d) Point 4

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(f) Point 6

(g) Point 7

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2.3

, MIL-STD-167-1A :2005(Type II) , . 2.3.1 1 Hz 1000 Hz , Hanning 1 Hz . Table 2 , Fig. 3 . 2.3.2 MIL-STD-167-1A:2005 . Fig. 7 , . , . (i) Point 9

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Fig. 8 Measurement position of motor bearing housing Fig. 7 Measurement result of motor bearing housing

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2.4

2.4.1 ,

,

, , , . , , . 2.4.2 9 , Fig. 6 160 Hz 10000 Hz . , 10 Hz ~ 750 Hz , 1 Hz Narrow

band Fig. 9 . Table

4 . , , . Narrow band 20 Hz 1X , 5 180 Hz, 339 Hz, 360 Hz, 539 Hz, 719 Hz . 180 Hz, 360 Hz, 539 Hz, 719 Hz 9 , .

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(a) Point 1

(b) Point 2

(26)

(d) Point 4

(e) Point 5

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(g) Point 7

(h) Point 8

(i) Point 9

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Direction Major frequency (Hz) Point 1 X axis 20 180 - 359 539 719 Y axis 20 180 - 359 - 719 Z axis 20 180 - 359 539 -Point 2 X axis 20 180 339 359 539 719 Y axis 20 180 - 359 - -Z axis 20 180 339 359 539 719 Point 3 X axis 20 180 - 359 - 719 Y axis 20 180 - - - -Z axis 20 180 - 359 539 719 Point 4 X axis 20 180 339 359 - -Y axis 20 180 - 359 539 719 Z axis 20 180 - 359 539 719 Point 5 X axis 20 180 339 359 - -Y axis 20 180 339 359 539 719 Z axis 20 180 339 359 539 719 Point 6 X axis 20 180 339 - 539 -Y axis 20 180 - 359 - -Z axis 20 180 - 359 539 -Point 7 X axis 20 180 339 359 - -Y axis 20 - - 359 - -Z axis 20 180 339 359 539 719 Point 8 X axis 20 180 - - - -Y axis 20 - - 359 - 719 Z axis 20 180 - 359 539 -Point 9 X axis 20 180 - 359 539 719 Y axis 20 180 - 359 - -Z axis 20 180 - 359 539 719

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3.

Narrow band , . UG NX 5.0 , ANSYS Workbench 12.1 , .

3.1

. . . . .

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3.1.1

.

 . (multi degree-of-freedom system) .

















 (1)

_  _ ₍₁₈₎ _ tan _ _ _ (19)  ,  .   .

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3.2

3.2.1

3 , (Initial model)

, 1 (Frist reinforcement

model) 2

, 2 (Second reinforcement model) 4

3 .

,

, ,

Table 5 .

Table 5 Material property

Item Value SS400 Density (kg/m3) 7860 Poisson's ratio 0.26 Spring Stiffness (N/mm) vertical 285 horizontal 313.5 Damping 0.05 Motor Mass (kg) 450 Pump Mass (kg) 31.8 Accumulator Mass (kg) 200

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3.2.2 5 N X , Y , Z , 5N 1X 20 Hz 10 Hz 750 Hz 10 Hz 1 9 3 (m/s2) . 3.2.3 (natural frequency) , Table 6 . 3 .   _



_ (20)

Table 6 Natural frequency of spring-mass model

Model Value of result (Hz)

Natural frequency of Spring-mass model

X axis Y axis Z axis

7.1 7.1 6.8 FE model modal frequency Initial model Frist reinforcement model Second reinforcement model 7.5 7.4 7.3

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3.3

3.3.1 . Fig. 10 3D . (a) Modeling (b) mesh

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Table 7 Comparison of major frequency(Initial model) 3.3.2 Table 7 . 6 , , , , .

Major frequency of test model　 Frequency of FE model　

No Frequency (Hz) No Frequency (Hz) 1 180 1 179.7 2 339 2 336.0 3 359 3 357.3 4 361.3 4 539 5 550.0 5 719 6 723.7 (a) 179.7 Hz

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(b) 336.0 Hz

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(d) 361.3 Hz

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3.3.3 3.2.2 Fig. 12, Fig. 13 , 380 Hz, 550 Hz, 598 Hz, 689 Hz, 732 Hz, 738 Hz . (300 Hz ~ 500 Hz) , 4 380 Hz , 4, 5 . 550 Hz , 598 Hz, 689 Hz, 732 Hz, 738 Hz . (f) 723.7 Hz

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(a) Point 1

(b) Point 2

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(d) Point 4

(e) Point 5

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(g) Point 7

(h) Point 8

(i) Point 9

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(a) Point 2, 4, 5, 9 (380 Hz)

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(c) Point 1, 7 (598 Hz)

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(e) Point 1, 4, 5, 6, 7, 8, 9 (732 Hz)

(f) Point 1, 4, 5, 6, 7, 8, 9 (738 Hz)

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3.4 1

3.4.1 Fig 14 1 3D , 10 mm , , , . (a) modeling (b) mesh

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Table 8 Result of modal frequency(Frist reinforcement model) No Frequency (Hz) No Frequency (Hz) 1 4.1 15 265.3 2 4.3 16 279.9 3 7.4 17 298.0 4 11.3 18 299.9 5 13.7 19 304.3 6 17.3 20 310.9 7 46.8 21 313.2 8 79.5 22 325.0 9 114.0 23 338.8 10 152.5 24 347.8 11 156.7 25 374.1 12 177.1 26 385.4 13 186.2 27 391.0 14 233.1 28 458.0 29 464.4 44 592.8 30 468.0 45 598.8 31 477.3 46 613.7 32 477.7 47 627.5 33 484.4 48 645.1 34 500.6 49 652.5 35 505.7 50 655.7 36 514.1 51 675.5 37 516.7 52 680.4 38 523.7 53 688.1 39 533.7 54 710.8 40 549.6 55 723.3 41 556.9 56 726.6 42 572.5 57 744.8 43 583.6 3.4.2 Table 8 1 . 6 1 5 .

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3.4.3 3.2.2 Fig. 15, Fig. 16 , 280 Hz, 298 Hz, 299 Hz, 300 Hz, 593 Hz, 599 Hz, 614 Hz, 711 Hz . , . 1 9 280 Hz, 298 Hz, 299 Hz, 300 Hz , , , . 593 Hz, 599 Hz, 614 Hz 380 Hz 4 1 593 Hz 599 Hz, 614 Hz . 711 Hz . (a) Point 1

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(b) Point 2

(c) Point 3

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(e) Point 5

(f) Point 6

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(h) Point 8

(i) Point 9

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(a) Point 1~9 (280 Hz)

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(c) Point 2, 7 (299 Hz)

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(e) Point 1, 2, 3, 7 (593 Hz)

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(g) Point 4, 6, 7 (614 Hz)

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(i) Point 2, 5, 7 (727 Hz)

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3.5 2

3.5.1 Fig 17 3D , 1 10 mm , , , . (a) modeling (b) mesh

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Table 9 Result of modal frequency(Second reinforcement model) No Frequency (Hz) No Frequency (Hz) 1 4.1 20 463.3 2 4.2 21 474.3 3 7.3 22 477.8 4 11.2 23 506.8 5 13.5 24 523.0 6 16.8 25 523.6 7 58.2 26 543.2 8 98.1 27 562.6 9 152.1 28 573.3 10 238.6 29 587.2 11 272.8 30 597.7 12 278.0 31 610.9 13 329.4 32 625.7 14 333.1 33 653.3 15 385.6 34 680.5 16 399.1 35 702.2 17 412.1 36 724.0 18 442.5 37 730.1 19 450.0 38 744.6 3.5.2 Table 9 . 1 5 4 . 3.5.3 3.2.2 Fig. 18, Fig. 19 , 330 Hz, 562 Hz, 702 Hz, 724 Hz 1 . 1 280 Hz, 298 Hz, 299 Hz, 300 Hz 2 , 599 Hz 614 Hz .

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(a) Point 1

(b) Point 2

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(d) Point 4

(e) Point 5

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(g) Point 7

(h) Point 8

(i) Point 9

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(a) Point 2, 6, 7, 8, 9 (330 Hz)

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(c) Point 4, 5, 9 (702 Hz)

(d) Point 3, 4, 5, 7, 9 (724 Hz)

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3.6

Fig. 20 3 . 1 9 , . . , . , . . , , .

(a) Initial model (b) Reinforcement model (c) Final model

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4.

.

4.1

Fig. 21 , 1 9 . (a) Point 1

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(b) Point 2

(c) Point 3

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(e) Point 5

(f) Point 6

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4.2

Fig. 22 Narrow band

180 Hz, 339 Hz, 360 Hz, 539 Hz, 719 Hz ,

. (h) Point 8

(i) Point 9

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(a) Point 1

(b) Point 2

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(d) Point 4

(e) Point 5

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(g) Point 7

(h) Point 8

(i) Point 9

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5.

, . . 1. 5 180 Hz, 339 Hz, 360 Hz, 539 Hz, 719 Hz , 20 Hz 1 , 180 Hz, 360 Hz, 539 Hz, 719 Hz 9 , . 2. , . 3. . 1 , .

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”, .

[8] , , 1999, , .

[9] , , , 2006, · .

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", .

[12] Qi Dalong, 2015, "A study on the vibration analysis of Marine Pump", Pukyong National University, Thesis for the Degree of Master of Engineering.

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[13] MIL-STD-740-1(SH), 1986, "Air-borne sound Measurements and Acceptance Criteria of Shipboard Equipment."

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[15] , 2003, , .