Examples_Ch 2_Compressor S. Y. B. Tech. Prod Engg. ME0223 SEM- IV Applied Thermodynamics & Heat Engines Compressor Examples Applied Thermodynamics & Heat Engines S.Y. B. Tech. ME0223 SEM - IV Production Engineering
Jan 19, 2015
Examples_Ch 2_Compressor
S. Y. B. Tech. Prod Engg.ME0223 SEM-IV Applied Thermodynamics & Heat Engines
Compressor
Examples
Applied Thermodynamics & Heat Engines
S.Y. B. Tech.
ME0223 SEM - IV
Production Engineering
Examples_Ch 2_Compressor
S. Y. B. Tech. Prod Engg.ME0223 SEM-IV Applied Thermodynamics & Heat Engines
Example 1A single-stage reciprocating compressor takes 1m3 of air per minute at 1.013 bar and 15 0C and delivers it at 7 bar. Assuming that the law of compression is PV1.35 = constant, and the clearance is negligible, calculate the indicated power.
Mass of air delivered per min. :
min/226.1)288()./287.0(
)1()/10013.1( 325
1
11 kgKKkgkJ
mmNX
TR
VPm
Delivery Temperature :
Kbar
barK
P
PTT
n
n
2.425013.1
7)288(
35.1
135.11
1
212
Indicated Work :
kWkJ
KKCkgkJkgTTRmn
nW
23.460
254min/254
)2882.475()./287.0(min)/226.1(35.1
135.1)(
112
….ANS
Examples_Ch 2_Compressor
S. Y. B. Tech. Prod Engg.
Example 2If the compressor in last example is driven at 300 rpm and is a single acting, single-cylinder machine, calculate the cylinder bore required, assuming a stoke to bore ration of 1.5:1.Calculate the power of the motor required to drive the compressor if the mechanical efficiency of the compressor is 85 % and that of the motor transmission is 90%.
ME0223 SEM-IV Applied Thermodynamics & Heat Engines
Volume dealt with per min. at inlet = 1 m3/min
5.1
400333.0)5.1(
400333.0
4222
X
XDDDLD
Hence, Vol. drawn in per cycle = 1/300 = 0.00333 m3/cycle = Cylinder Volume
Thus, cylinder bore, D = 0.1414 m or 141.4 mm ….ANS
Power input to the compressor = kWkW
53.585.0
23.4 ….ANS
Examples_Ch 2_Compressor
S. Y. B. Tech. Prod Engg.ME0223 SEM-IV Applied Thermodynamics & Heat Engines
An air compressor takes in air at 1 bar and 20 ºC and compresses it according to law PV1.2
= C. It is then delivered to a receiver at a constant pressure of 10 bar. R = 0.287 kJ/kg.K. Determine :1.Temperature at the end of compression.2.Work done and heat transferred during compression per kg of air.
Example 3
P1
P2
V1V2
3 2
4 1
CVP 2.1
Delivery Temperature :
CKbar
barK
P
PTT
n
n
1574301
10)293(
2.1
12.11
1
212
Work done :
airofkgkJ
KCkgkJkg
P
PTRm
n
nW
n
n
/236
1
101)293()./287.0(min)/1(
2.1
12.1
11
2.1
12.1
1
1
21
….ANS
Examples_Ch 2_Compressor
S. Y. B. Tech. Prod Engg.ME0223 SEM-IV Applied Thermodynamics & Heat Engines
Example 3….contd
P1
P2
V1V2
3 2
4 1
CVP 2.1
Heat Transferred :
airofkgkJ
K
n
RCTT
n
TTRTTC
n
VPVPTTC
WUQ
V
V
V
/)23.98(
12.1
287.0718.0)293430(
1)(
1
)()(
1)(
12
1212
112212
….ANS
Examples_Ch 2_Compressor
S. Y. B. Tech. Prod Engg.
Example 4Following data relate to a performance test of a single-acting 14 cm X 10 cm reciprocating compressor:Suction Pressure =1 bar Suction temperature = 200 CDischarge Pressure = 6 bar Discharge temperature = 180 0C Speed of compressor = 1200 rpm Shaft Power = 6.25 kWMass of air delivered =1.7 kg/min
Calculate the following:1. The actual volumetric efficiency. 4. The indicated power.2. The isothermal efficiency. 5. The mechanical efficiency.3. The overall isothermal efficiency.
ME0223 SEM-IV Applied Thermodynamics & Heat Engines
P1
P2
V1V2
3 2
4 1
CVP n min/8473.1)1200()1.0()14.0(
4
4
32
2
mrpmXmm
NXLDVd
….for single-acting compressor
min/4295.1
101
)293()./287.0()7.1(
3
51
1
m
X
KKkgkJkg
P
TRmFAD
Examples_Ch 2_Compressor
S. Y. B. Tech. Prod Engg.
Example 4….contd
ME0223 SEM-IV Applied Thermodynamics & Heat Engines
P1
P2
V1V2
3 2
4 1
CVP n
%38.77100min/8473.1
min/4295.1100
3
3
Xm
mX
V
FAD
dvol ….ANS
32.1
)1/6(ln
293/453ln1
1
)/(ln
/ln1
12
12
1
1
2
1
2
nnPP
TT
n
n
P
P
T
T n
n
Indicated Power :
kW
KCkgkJkg
P
PTRm
n
nW
n
n
346.5
1
61)293()./287.0(sec/
60
7.1
32.1
132.1
11
32.1
132.1
1
1
21
….ANS
Examples_Ch 2_Compressor
S. Y. B. Tech. Prod Engg.
Example 4….contd
ME0223 SEM-IV Applied Thermodynamics & Heat Engines
P1
P2
V1V2
3 2
4 1
CVP n
Isothermal Power :
kW
bar
barKCkgkJkg
P
PTRmWiso
269.4
1
6ln)293()./287.0(sec/
60
7.1
ln1
21
%85.79100346.5
269.4100 X
kW
kWX
PowerIndicated
PowerIsothermaliso
….ANS
%5.8510025.6
364.5100 X
kW
kWX
PowerShaft
PowerIndicatedmech
….ANS
%3.6810025.6
269.4100)( X
kW
kWX
PowerShaft
PowerIsothermaloveralliso
….ANS
Examples_Ch 2_Compressor
S. Y. B. Tech. Prod Engg.ME0223 SEM-IV Applied Thermodynamics & Heat Engines
Example 5A single-stage double-acing air compressor is required to deliver 14 m3 of air per min measured at 1.013 bar and 15 OC. the delivery pressure is 7 bar and the speed 300 rpm. Take the clearance volume as 5 % of swept volume with the compression and expansion index of n = 1.3. Calculate:1. Swept volume of the cylinder 2. Indicated power 3. Delivery temperature.
Swept Vol. Vs = V1 – V3 = V1 – Vc = V1 – 0.05 Vs
P1
=1.013 bar
P2
=7 bar
V1V4
6 2
5 1
CVP 3.1
3
4
V3
Swept Volume, V1-V3=Vs
V3=Vc
= 0.05 Vs
288 K
Vol. induced per cycle = (V1 – V4 )
V1 = 1.05 Vs
lecycmsidesXrpm
mVV /0233.0
2300
min/14)( 3
3
41
423.4013.1
705.1
3.1
11
1
2
3
41
bar
bar
P
P
V
VandVV
n
S
Examples_Ch 2_Compressor
S. Y. B. Tech. Prod Engg.ME0223 SEM-IV Applied Thermodynamics & Heat Engines
Example 5….contd
V4 = 4.423 V3 = 4.423 X 1.05 Vs = 0.221 Vs (V1 – V4 ) = 1.05 Vs – 0.221 Vs = 0.0233 m3
33
0281.0)221.005.1(
0233.0m
mVS
….ANSSwept Volume,
Delivery Temperature : Kbar
barK
P
PTT
n
n
450013.1
7)288(
3.1
13.11
1
212
….ANS
Indicated Power :
kW
bar
bar
X
mmNX
P
PVVP
n
nW
n
n
56.57
0132.1
71
6010
min)/14()/10013.1(
3.1
13.1
11
3.1
13.1
3
325
1
1
2411
….ANS
Examples_Ch 2_Compressor
S. Y. B. Tech. Prod Engg.ME0223 SEM-IV Applied Thermodynamics & Heat Engines
Example 6A four-cylinder double-acting compressor is required to compress 30 m3 / min of air at 1 bar and 27 0C to a pressure of 16 bar. Determine the size of motor required and cylinder dimensions if the following data is given :Speed of compressor = 320 rpm. Clearance volume = 4 % Stroke : Bore ratio = 1.2 Mechanical Efficiency = 82 %Index = 1.32Assume no pressure change in suction valves and air gets heated by 12 0C during suction stroke.
Net Work done :
kW
bar
bar
X
mmNX
P
PVVP
n
nW
n
n
64.197
1
161
6010
min)/30()/101(
32.1
132.1
11
32.1
132.1
3
325
1
1
2411
….ANS
Motor Power : kWWmech
24182.0
64.19764.197
….ANS
Examples_Ch 2_Compressor
S. Y. B. Tech. Prod Engg.
Example 6….contd
ME0223 SEM-IV Applied Thermodynamics & Heat Engines
Vol. Efficiency :
%6.68)39273(
)27273(.)1(
)1(
1
1604.004.01
.1
32.1
1
1
1
2
K
K
bar
barX
bar
bar
T
T
P
PX
P
Pkk
inside
atm
atm
insiden
vol
Swept Vol. per cylinder :
33
01708.0686.0
1.)320()2(
1.)4(
min)/30(m
rpmsidescylinders
m
)2.1(4
01708.04
22 DDLD
mmmXL
mmmD
6.315263.02.1
263263.0
….ANS
….ANS
Examples_Ch 2_Compressor
S. Y. B. Tech. Prod Engg.ME0223 SEM-IV Applied Thermodynamics & Heat Engines
Example 7 Air at 103 kPa and 27 0C is drawn in L.P. cylinder of a two-stage air compressor and is isentropically compressed to 700 kPa. The air is then cooled at constant pressure at 37 0C in an intercooler and is then again compressed isentropically to 4 MPa in the H.P. cylinder, and is deliverer at this pressure. Determine the power required to run the compressor if it has to deliver 30 m3 of air per hour measured at inlet conditions.
P1 = 103 kPa
P3 = 4 MPa
3
2
1
CVP
P2 = 700 kPa
L.P.
H.P.
Volume
Mass of air delivered per min. :
hrkgKKkgkJ
hrmmNX
TR
VPm /89.35
)300()./287.0(
)/30()/10103( 323
1
11
Temperature for compression process 1-2’ :
KkPa
kPaK
P
PTT 7.518
103
700)300(
4.1
14.11
1
21'2
Temperature for compression process 2-3 :
KkPa
MPaK
P
PTT 1.510
700
4)310(
4.1
14.11
2
323
Examples_Ch 2_Compressor
S. Y. B. Tech. Prod Engg.ME0223 SEM-IV Applied Thermodynamics & Heat Engines
Work required to run the compressor :
kW
KKKKCkgkJhrkg
TTTTRm
TTRmTTRmW
194.4
)3101.510()3007.518()./287.0()/89.35(4.1
14.1
)()(1
)()(1
231'2
231'2
….ANS
Example 7….contd
Examples_Ch 2_Compressor
S. Y. B. Tech. Prod Engg.ME0223 SEM-IV Applied Thermodynamics & Heat Engines
Example 8
P1 = 1 bar
P3 = 40 bar
3
2
1
CVP 3.1
P2 = 6 bar
L.P.
H.P.
Volume
A trial on a two-stage single-acting reciprocating compressor gave the following data :Free air delivered =6 m3/min Delivery Pr. = 40 barAtm. Pr. and Temp. = 1 bar 27 ºC Speed = 400 rpm Intermediate Pr. = 6 bar Temp. at inlet to 2nd stage = 27 ºC Law of Compression =PV1.3 = C Mechanical Efficiency = 80 %Stroke of L.P. = Stroke of H.P. = Diameter of L.P.
Assuming Vol. Efficiency of 100 %,
mmLD
XDXDRPMXLXDFAD
PLPL
PLPLPLPL
3.267
4004
64
....
..2....
2..
….ANS
Swept Vol. of H.P. cylinder = Vol. of air at 6 bar, 27 ºC
mmD
XXD
RPMXLXDm
PH
PH
PHPH
109
4002673.04
4min/1
..
2..
..2
..3
….ANS
Examples_Ch 2_Compressor
S. Y. B. Tech. Prod Engg.ME0223 SEM-IV Applied Thermodynamics & Heat Engines
Example 8….contd
Indicated Work :
kW
bar
bar
bar
bar
X
mmNX
ngIntercooliPerfectTTP
P
P
PVP
n
nW
n
n
n
n
42.58
6
40
1
62
6010
min)/6()/101(
3.1
13.1
......21
3.1
13.1
3.1
13.1
3
325
13
1
2
3
1
1
211
….ANS
Examples_Ch 2_Compressor
S. Y. B. Tech. Prod Engg.ME0223 SEM-IV Applied Thermodynamics & Heat Engines
A two-stage single-acting reciprocating air compressor takes in air at the rate of 0.2 m3/sec. The intake pressure and temperature are 0.1 MPa and 16 ºC. The air is compressed to a final pressure of 0.7 MPa. The intermediate pressure is ideal and intercooling is perfect. The compression index in both stages is 1.25 and the compressor runs at 600 rpm. Neglecting clearance, determine :1.Intermediate Pr. 2. Total Vol. of each cylinder.3. Power required to drive compressor 4. Rate of heat rejection in intercooler
Example 9
Intermediate Pr., P2 : ngIntercooliPerfectMPaPPP ....2646.0)7.0()1.0(312 ….ANS
Vol. of cylinder 1, Vs1 :3
1111 02.02.060
600
60mVXVV
NXV SSS ….ANS
Vol. of cylinder 2, Vs2 :
32
3
2
2
1122211
00756.0
2646.0
)02.0()1.0(
mV
MPa
mMPaV
P
VPXVVPVP
S
S
SSSS
….ANS
Examples_Ch 2_Compressor
S. Y. B. Tech. Prod Engg.ME0223 SEM-IV Applied Thermodynamics & Heat Engines
Power Required :
kW
MPa
MPammNXX
ngIntercooliPerfectP
PVP
n
nP
n
n
96.42
1.0
7.01
10
sec)/2,0()/101.0(
125.1
25.12
......11
2
25.1
125.1
3
326
2
1
1
311
….ANS
Example 9….contd
Mass of air handled : sec/241.0)289()./287.0(
sec)/2.0()/101.0( 326
1
11 kgKKkgkJ
mmNX
TR
VPm
Delivery Temperature : KMPa
MPaK
P
PTT
n
n
1.3511.0
2646.0)289(
25.1
125.11
1
212
Heat rejected in Intercooler :
kWKKKkgkJkg
TTCm P
4.152891.351)./005.1(sec)/241.0(12
….ANS
Examples_Ch 2_Compressor
S. Y. B. Tech. Prod Engg.ME0223 SEM-IV Applied Thermodynamics & Heat Engines
Example 10A two-stage air compressor with complete intercooling delivers air to the mains at a pressure of 30 bar, the suction conditions being 1 bar and 15 0C. if both cylinders have same stroke, find the ratio of cylinder diameter for the efficiency of compression to be maximum. Assume index of compression to be 1.3.
P1
P3 3
2
1
CVP 3.1
P2
L.P.
H.P.
Volume
2’5
6
42
1
..
..
2..
2..
2
1
4
4V
V
D
D
LD
LD
V
V
PH
PL
PH
PL
3.1/1
1
2
'2
13.1'22
3.111
3.1
P
P
V
VVPVPCVP
For max. efficiency : barPPP 48.5)30()1(312
7.348.5 3.1/1
'2
1 V
V
Examples_Ch 2_Compressor
S. Y. B. Tech. Prod Engg.ME0223 SEM-IV Applied Thermodynamics & Heat Engines
Example 10
DAm /4
Delivery Temperature : Kbar
barK
P
PTT
n
n
4.4261
48.5)288(
3.1
13.11
1
21'2
For Const. Pr. Process 2 – 2’ : 48.1290
4.426
2
'2
2
'2
'2
'2
2
2 K
K
T
T
V
V
T
V
T
V
Thus, we get : 476.548.17.32
'2
'2
1
2
1 XV
VX
V
V
V
V
Hence : 34.2476.52
1
..
.. V
V
D
D
PH
PL ….ANS