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Research Papers

Experimental Study on the Effect of Diffuser Vane Setting Angle on Centrifugal Compressor Performance

[+] Author and Article Information
Hideaki Tamaki

Corporate Research & Development,
IHI Corporation 1,
Shin-Nakahara-Cho,
Isogo-Ku, Yokohama 235-8501, Japan
e-mail: hideaki_tamaki@ihi.co.jp

Contributed by the International Gas Turbine Institute (IGTI) of ASME for publication in the JOURNAL OF TURBOMACHINERY. Manuscript received July 11, 2016; final manuscript received October 20, 2016; published online February 1, 2017. Editor: Kenneth Hall.

J. Turbomach 139(6), 061001 (Feb 01, 2017) (13 pages) Paper No: TURBO-16-1151; doi: 10.1115/1.4035212 History: Received July 11, 2016; Revised October 20, 2016

The effect of the diffuser vane setting angle on the performance of a centrifugal compressor was experimentally investigated. Seven different vaned diffusers were tested with the same impeller. In order to evaluate the vaned diffusers under the same flow range and diffuser inlet conditions, all the diffusers were designed to have the same throat area, the same diffuser height. and the same vane inlet position. The first tests were performed by a compressor with a volute. In this case, the diffuser outlet conditions were varied along the circumferential directions due to the nonaxisymmetric geometry of the volute. In the second tests, four of the seven vaned diffusers were tested using a compressor with a collector. In this case, the diffuser outlet conditions were more uniform along the circumferential directions compared to the tests using the compressor with the volute. The effect of the vane setting angle on the stage characteristics and diffuser performance as well as the effect of the circumferential distortion caused by the volute on the stage characteristics are presented. The impact of the incidence loss on the vaned diffuser performance is discussed using 1D vaned diffuser performance modeling. Comparisons of the 1D predictions and the tests results show the incidence loss has a strong influence on vaned diffuser performance.

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References

Figures

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Fig. 1

Meridional view of tested impeller

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Fig. 2

Tested compressor performance: (a) stage pressure ratio with optimal vaned diffuser VD01, (b) stage efficiency with optimal vaned diffuser VD01, and (c) stage pressure ratio with Vaneless diffuser, VD01, VD02, and VD3

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Fig. 3

Examples of tested diffusers and locations of static pressure holes upstream of throat (vane geometry; VD4): (a) explanation of parameters in Table 1 and Table 2, (b) tested diffusers (top left, VD1; top right, VD3; bottom left, VD5; bottom right, VD7), and (c) locations of static pressure holes

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Fig. 4

Stage characteristics: (a) total-to-total pressure ratio and (b) efficiency

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Fig. 5

Static pressure at vaned diffuser outlet

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Fig. 6

Change of stage peak efficiency with vane setting angle

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Fig. 7

Variation of the surge flow rate divided by the surge flow rate of the compressor with VD2

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Fig. 8

Flow angle and total pressure distribution at Mu = 1.35: (a) flow angle and (b) total pressure

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Fig. 9

Mass averaged total pressure, mass averaged flow angle, impeller efficiency and static pressure at diffuser inlet at Mu = 1.35: (a) total pressure and efficiency and (b) flow angle and static pressure

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Fig. 10

Pressure recovery factor from diffuser inlet to vane outlet

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Fig. 11

Pressure recovery factor from diffuser inlet to throat

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Fig. 12

I Pressure recovery factor from throat to vane outlet

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Fig. 13

Variation of Cp2 with AR

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Fig. 15

Pressure recovery factor: (a) pressure recovery factor from vane inlet to vane outlet with incidence loss, (b) pressure recovery factor from vane inlet to vane outlet without incidence loss, (c) pressure recovery factor from vane inlet to throat, and (d) pressure recovery factor from throat to vane outlet

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Fig. 16

Circumferential static pressure distribution in a vaneless diffuser at 1.07 R2 at Mu = 1.35

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Fig. 17

Static pressures in two different vaned diffuser passages (Passage-1 and Passage-2) of VD5 at Mu = 1.35: (a) volute and (b) collector

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Fig. 18

Stage characteristic (P06/P01) compressor with volute and with collector

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Fig. 19

Ratio of surge flow rate of collector divided by surge flow rate of volute

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Fig. 20

Change of stage peak efficiency with vane setting angle

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Fig. 21

Variation of surge flow rate divided by surge flow rate of the compressor with VD3

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Fig. 22

Work coefficient of compressor with volute and with collector

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Fig. 23

Stage characteristics of compressor with volute and with collector (vaneless diffuser)

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Fig. 24

Work coefficient of compressor with volute and with collector (vaneless diffuser)

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Fig. 25

Diffuser pressure recovery factor: (a) pressure recovery factor from diffuser inlet to vane outlet, (b) pressure recovery factor from diffuser inlet to diffuser throat, and (c) pressure recovery factor from diffuser throat to vane outlet

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Fig. 26

Total pressure, impeller efficiency, flow angle and measured static pressure at diffuser inlet at Mu = 1.35: (a) total pressure and impeller efficiency and (b) flow angle and (measured) static pressure

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Fig. 27

R Schematic of impeller surrounded by circumferentially nonuniform flow field

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Fig. 28

Effect of volute size on work coefficient of turbocharger compressor with impeller diameter of 50 mm: (a) stage characteristics and (b) work coefficient and parameters in Table3

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Fig. 29

Effect of circumferential nonuniformity of flow fields on work coefficient: (a) tested compressor setup, (b) circumferential static pressure distribution, and (c) work coefficient

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