prediction of leakage flow of radial clearance in a
TRANSCRIPT
Clean energy & Micro spray application
07 13, 2016
2016 Purdue Conferences
1
July 11-14, 2016, Purdue, United States of America
Prediction of Leakage Flow of Radial Clearance
in A Rolling Piston Rotary Compressor
Graduate School of Mechanical Engineering, Pusan National University, Korea
Geon-woo Kim, Ki-youl Noh, Byung-chae Min, Sang jin Song, Sang-kyung Na, Tae-seung Yoon
Kenichiro teshima
Interdisciplinary Graduate School of Engineering Sciences, Kyushu University, Korea
Jang-sik Yang
Rolls-Royce University Technology Centre, Pusan National University, Korea
Gyung-min Choi, Duck-jool Kim
Department of Mechanical Engineering, Pusan National University, Korea
2Clean energy & Micro spray application
Thermodynamics
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1 3 54 6CONTENTS
▣ Back ground
Clean energy & Micro spray application
▷ Increasing global power consumption
Ref. World Energy Outlook 2014 New Policies scenario (IEA)
▷ Numerical compressor simulation
▷ Needs for improving the efficiency of compressors
Motor efficiency
Volumetric efficiency
Indicated efficiency
Mechanical efficiency
Compressor
Efficiency
Reduce the cost and time of development
DynamicsGeometric
characteristics
Need for accurate prediction
VariousCapacity
Various operating condition
Various geometric
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1 3 54 6CONTENTS
▣ Back ground
Clean energy & Micro spray application
▷ Compressor efficiency
����� = �� × �� × ���� × ������ η���� ∶ compressorefficiency
η" ∶ volumetricefficiency
η'()' ∶ indicatedefficiency
�,�-:motorefficiency
η�/�0:mechanicalefficiency23 =
4566789
4566:;
▷ Type of leakage
70 %
① Radial clearance between wall of rolling piston and cylinder
② Clearances between the faces of the rolling piston and head walls of the cylinder
③ Faces of the sliding vane and head walls of the cylinder
④ Clearances between sides of the sliding vane and side cylinder
Oil Roller rotate FrictionOperating condition
▷ Influenced Factors
GeometricFrictionOperating condition
Geometric
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▣ Previous research
Clean energy & Micro spray application
(1985) (1990) (2012)
Insufficient investigation for consideration of geometric characteristics and operation condition of compressor
Flow pattern (single) & Friction
Flow pattern (two phase) & roller motion
Flow pattern (two phase)& bubble
Ref) Yanagisawa, T., Shimizu, T. Leakage losses in a rolling piston type rotary compressor, I. Radical clearance on the rolling piston,/int Refrig 8 (1985) 75-84
Ref) C.M.N.F et al. Considerations about the leakage through the minimal clearance in a rolling piston compressor, Int compressor engineering conference (1990) 780
Ref) Jose Luiz Gasche et al. A model to predict R134a refrigerant leakage through the radial clearance of rolling piston compressor, Int Ref 35(2012) 2223-2232
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1 3 54 6CONTENTS
▣ Objective
- Flow chart -
Leakage Modeling
m< � =�P?A2k
k C 1 RT?
P)
P?
GH
CP)
P?
HIJH
• Operating condition of compressor
• Various geometric of radial clearance
• Applicability
Experiments CFD simulation
KL � MNO, QR , ST, SUV
Functionalization ofFlow coefficient
Investigation characteristics of flow coefficient under various condition
Clean energy & Micro spray application
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1 3 54 6CONTENTS
▣ Mass flow rate through the radial clearance
For W�� ≥ W�/WZ
For W�� < W�/WZ
m< = C"P?A2k
k − 1 RT?
P)
P?
GH
−P)
P?
HIJH
m< = C"P?Ak
RT?
2
k + 1
HIJG H^J
- Isentropic and one-dimensional compressible flow through the simple orifice
_ Area of the radial clearance (`G)
=� Flow coefficient of the radial clearancek Specific heat ratio4< Mass flow rate (kg/s)W�� Critical pressure ratio
W� Downstream pressure (Pa)W� Pressure ratioWZ Upstream pressure (Pa)R Gas constant ((N*m)/(kg*K))aZ Upstream temperature (K)
The flow coefficient b3 is affected by flow area of radial clearance, upstream pressure and pressure ratio
WZW�
Suction port Discharge port
(1)
(2)
(3)
Mas
s flow
rat
e
W�/WZ
W�� =c
d + e
dd^e
Clean energy & Micro spray application
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▣ Schematic diagram of experimental set-up
W(= WZ) W�Z�(= W�)
◈ Experimental conditions
Height of the cylinder 19.989 mm
Width of the radial clearance 20 μm
Inlet pressure (= f8) 3~8 bar
◈ measuring equipment
Pressure transducer KISTLER, 4260A
Thermocouple K-type
Mass flow rate Bubble meter
◈ Assumptions of the experiment
1 Working fluid (Only Nitrogen)
2 Incompressible flow
3 Steady state flow
Width of radial clearance: 20 μm
Height of radial clearance: 19.989 mm
Clean energy & Micro spray application
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1 3 54 6CONTENTS
(CFD : Computational Fluid Dynamics)
2-D analysis (Incompressible steady state flow)
Viscous model Realizable k-ε model
Inlet boundary condition Pressure inlet
Outlet boundary condition Pressure outlet
Pressure-Velocity coupling Coupled
In order to reduce time of computation, the geometry of experimental device was simplified
Simplify
▣ Setting for CFD simulation
Clean energy & Micro spray application
▣ Calculation range for calculating the mass flow rate
Upstream pressure ~ 30 bar
Pressure ratio 0.1, 0.5, 0.9
Width of radial clearance 10 ~ 60 μm
Height of radial clearance 5 ~ 30 mm
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1 3 54 6CONTENTS
5.1 Validation of CFD simulation
▣ Modeling the geometry of radial clearance based on data of SEM (Scanning Electron Microscope)and clearance gauge for CFD simulation
0.0 0.2 0.4 0.6 0.8 1.00.00000
0.00025
0.00050
Mas
s flo
w r
ate
(kg/
s)
Pressure ratio (Pd/Pu)
Exp. 4 bar Exp. 6 bar Exp. 8 bar CFD. 4 bar CFD. 6 bar CFD. 8 bar
Average error : 2.46 %
Maximum error: 3.53 %
Average error : 3.01 %
Average error : 2.11 %
Mass flow rate through the radial clearance obtained by CFD simulation showed tolerable errorsfor predicting the leakage flow rate
Clean energy & Micro spray application
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5.2 Functional formula of flow coefficient
• Radius of cylinder : 25 mm • Radius of roller : 20 mm • Height of radial clearance : 20 mm
▣ Results of CFD simulation with various width of radial clearance and upstream pressure
(a) : 10 μm (b) : 20 μm
Clean energy & Micro spray application
(c) : 40 μm (d) : 60 μm
Flow coefficient at the radial clearance was affected by change of area of radial clearance, pressure ratio and upstream pressure
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1 3 54 6CONTENTS
5.2 Functional formula of flow coefficient
• Radius of cylinder : 25 mm • Radius of roller : 20 mm
▣ Results of CFD simulation with various height of radial clearance
(a) : 10 μm (b) : 20 μm
Clean energy & Micro spray application
(c) : 40 μm (d) : 60 μm
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5.2 Functional formula of flow coefficient
• Radius of cylinder : 25 mm • Radius of roller : 20 mm
▣ Results of CFD simulation with various Height of radial clearance
gh =ijk
f
◈ Hydraulic diameter
lm ∶ nopqrsQtuptr`vwvq
Ox ∶ Kqyzzzvuwty{rQrqvr
S ∶ |vwwvp}vqt`vwvqyMw~vuqyzzzvuwty{
5.0E-3 1.0E-2 1.5E-2 2.0E-2 2.5E-2 3.0E-20.0
5.0E-5
1.0E-4
1.5E-4
Hyd
rau
lic d
iam
eter
(m
)
Height of radial clearance (m)
㎛ 10 ㎛ 20 ㎛ 40 ㎛ 60
Flow coefficient at the radial clearance was not affected by change of height of radial clearance
�< = =�WZ�hcd
d − e �aZ
W�
WZ
cd
−W�
WZ
dIed
KL = � + O ∗ log(�v)
Discharge flow coefficient through a venturi flow meter
Ref Colter L. Hollingshead., Discharge coefficient performance of venturi, standard concentric orifice plate, v-cone, and wedge flow meters at small reynolds numbers, All graduate theses and dissertations. (2011) pp869
Clean energy & Micro spray application
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5.2 Functional formula of flow coefficient
• Width of radial clearance : 40 μm
▣ Results of CFD simulation with various diameter ratio
• Height of radial clearance : 20 mm
• Diameter of cylinder : 25 mm • Upstream pressure : 4 bar
QR =2���x
v 1 − �G J G⁄� = 1 − �/v
Ref) Yanagisawa, T., Shimizu, T. Leakage losses in a rolling piston type rotary compressor, I. Radical clearance on the rolling piston,/ntJ Refrig 8 (1985) 75-84
◈ Friction length
25/18 25/19 25/20 25/210.008
0.009
0.010
0.011
0.012
Fri
ctio
n le
ng
th (
m)
Ratio of Diameter
0.0 0.2 0.4 0.6 0.8 1.00.0
0.2
0.4
0.6
0.8
1.0
Flo
w c
oeffi
cien
t
Pressure ratio (Pd/Pu)
25/18 25/19 25/20 25/21
Friction length increase 0.00091 m Flow coefficient decrease 0.03
Clean energy & Micro spray application
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5.3 Numerical compressor simulation
Clean energy & Micro spray application
▣ Compressor calorimeter experiment ▣ Compressor calorimeter experiment
Width of radial clearance
Upstream pressure
Pressureratio Friction length
�< = =�WZ_cd
d− e �aZ
W�
WZ
cd
−W�
WZ
dIed
▷ Functional formula
▷ 0.3 (suggested by previous work)
50
60
70
80
90
100
Eff
icie
ncy
(%
)
EXP 0.3 FUNC
50
60
70
80
90
100
Eff
icie
ncy
(%
)
EXP 0.3 FUNC
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1 3 54 6CONTENTS
5.3 Numerical compressor simulation
▣ Results of the compressor performance simulation
Clean energy & Micro spray application
Case 1 Case 2Suction pressure(bar, absolute) 9.95 9.95
Discharge pressure(bar, absolute) 33.8 33.8
Capacity of Comp. (cc) 14.1 12.5Comp. type Twin rotary Twin rotary
Frequency (Hz)
(a) Case 1
Frequency (Hz)
(b) Case 2
-2.03 %
Volumetric Mechanical & Indicated Compressor
40 60 80 40 60 80 40 60 80
Volumetric Mechanical & Indicated Compressor
40 60 80 40 60 80 40 60 80
-3.16 %-1.57 % +0.10 %
+2.29 %-2.17 %
-1.93 % -0.94 %-3.70 %
-7.84 %-7.21 %
-5.63 %
+5.64 %+5.88 %+2.51 %
-1.89 %-1.76 %
-3.26 %-4.74 %
-5.38 %-2.38 %
+0.91 %+2.76 %
-2.21 %
-3.88% -2.77 %-4.53%
-10.76 %-10.46 %
-6.97 %
+5.60 %+6.19 % +2.81 %
-4.15 % -4.34 %-4.36 %
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5.3 Numerical compressor simulation
▣ Results of the compressor performance simulation
Clean energy & Micro spray application
Case 3Suction pressure(bar, absolute) 10.15
Discharge pressure(bar, absolute) 23.37
Capacity of Comp. (cc) 14.1Comp. type Twin rotary
Frequency (Hz)
(c) Case 3
50
60
70
80
90
100
Eff
icie
ncy
(%
)
EXP 0.3 FUNC
Volumetric Mechanical & Indicated Compressor
40 60 80 40 60 80 40 60 80
-5.42 %-5.89 % -4.17 %
-9.52 %-7.11 %
-12.01 %
-15.23 %-12.61 %
-15.70 %
-7.51 %-7.64 %
-4.75 %
-8.89 %
-6.82 %
-12.51 %
-16.54 %-13.94 %
-16.32 %
�< = =�WZ_cd
d− e �aZ
W�
WZ
cd
−W�
WZ
dIed
Need for consideration of other factors
Friction
Operating conditionGeometric
Prediction of leakage through the radial clearance
Friction
Geometric Operatingcondition
Roller rotate Oil
Will investigate the sensitivity of influence factors of leakage through the radial clearance
Prediction of leakage through the radial clearance
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1 3 54 6CONTENTS
Clean energy & Micro spray application
The developed functional formula is helpful for predict the performance of compressor in the design process of novel compressor.
In this paper, the flow coefficient through the radial clearance in the rolling piston type rotary compressor was functionalized. The results are summarized as follows.
1. The functional formula of flow coefficient through the radial clearance was developed with consideration about operating of compressorand geometric characteristics.
2. The range of flow coefficient is from 0.08 to 0.85 under the various widthof radial clearance (10 μm - 60μm) and upstream pressure (4 bar – 30 bar)and different from 0.3 under the various operating condition.
3. The results of compressor performance with functional formula showedmore accuracy than results with 0.3
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Thank you for your attention!
Clean energy & Micro spray application