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ENERGY
Process Integration Scenario in SAP PI 7.1
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This paper focuses on energy efficient routing protocols of wireless sensor network for the crop monitoring of precision agriculture. Precision agriculture can be defined as the advanced technology which is used the art and science to enhance crop pr
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Outline Smith: Chemical Process Design and Integration (Chapters 16-22) Kemp: Pinch Analy Kemp: Analysis sis and Proce Process ss Integrati Integration on (Chap (Chapter ter 9 9))
➢
Process Integration
Systematic Approach for Chemical Process Design How do we go about the design of a chemical process?
➢
for Efficient Use of Energy
What Is Process Integration? Onion model for process integration
Cheng-Liang Chen
PSE
➢
Pinch Analysis: Targeting Heat Recovery in Processes
➢
Pinch Design Method for Heat Recovery Systems
➢
A Pinch Study Performed on A Major Operating Plant
➢
Utility Selection for Individual Processes
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Heat Integration for Individual Processes
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Putting It into Practice and Concluding Remarks
LABORATORY
Department of Chemical Engineering National TAIWAN University
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The Problem Table and Grand Composite Curve
Utility Selection for
Individual Processes
3
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The Problem Table and Grand Composite Curve
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The Problem Table and Grand Composite Curve
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The Problem Table and Grand Composite Curve
The
Grand Composite
gives the hot and cold utility requirements of the process both in Enthalpy and Temperature
Grand Composite Curve shows the utility requirements both in enthalpy and temperature terms ⇒ interface between the process and the utility system T ∗
Add Hot Utility
245
7.5
235
9 .0
195
3 .0
185
4 .0
145
0
75
14.
35
12.
25
10.
∆T int
—
—
——
————
——
10
+0.15
+1.5
——
————
——
40
−0.15
−6.0
75
—
230
⇓
⇑
200
190
200
——
————
——
⇓
⇑
⇓
10
+0.10
+1.0
180
190
180
190
——
————
——
⇑
⇓
⇑
⇓
40
−0.10
−4.0
150
140
150
——
————
——
⇓
70
+0.20
+14.
80
——
————
——
40
−0.05
−2.0
——
————
——
10
−0.20
−2.0
——
————
——
—
⇑
⇓
70
80
⇑
⇓
30
40
—
—
—
⇑ 25
20
CP
0.2
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—
—
—
0.15
0.3
0.25
Surplus/ Defict
∆H int
2 40
145 140
35
10
The Grand Composite Curve
—
CP H −CP C
4
⇓ 235
3
—— Surplus
⇓
——
⇓ ∆H 2
——
⇓
——
⇓ ∆H 4
——
7.5
+1.5
9.0
−4.5
3.0
−3.5
4.0
⇓
−7.5
0
+6.5
14.
+4.5
12.
+2.5
10.
∆H 5
——
⇓
Defict
∆H 6
——
⇓
Defict
∆H 7
——
0
Add Hot Utility
∆H 3
Defict
Surplus
Cascade Surplus
∆H 1
Defict
Surplus
Hot Utility
⇓
CW
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Grand Composite Curve with Alternative Utility Two levels of steams: 240oC, 180oC
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Grand Composite Curve with Alternative Utility Hot oil with T S = 280oC , C p = 2.1 kJ·kg−1· K−1 Minimum flow rate: steepest slope and min. return temperature
Flue Gas: Stack Temperature Limited by Acid Dew Point or Process Away from the Pinch
Increasing the theoretical flame temperature by reducing excess air or combustion air pre-heat reduces the stack loss Chen CL
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Flue Gas Matched Against the Grand Composite Curve of the Illustrative Process
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Solution: ➢
Assigning ∆T min contributions to streams: The process streams are assigned a contribution of 5 oC and flue gas a contribution of 25 oC
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Starting point of flue gas: 1800oC ⇒ 1775oC on grand composite curve
➢
The process is to have its hot utility supplied by a furnace. The theoretical flame temperature for combustion is 1800oC, and the acid dew point for the flue gas is 160 oC. Ambient temperature is 10oC. Assume ∆T min = 10oC for process-to-process heat transfer but ∆T min = 30oC for flue-gas-to-process heat transfer. Calculate the fuel required, stack loss, and furnace efficiency.
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The flue gas can be cooled to pinch temperature (T ∗ = 145oC) before venting to atmosphere o ⇒ actual stack temperature = 145 + 25 = 170 > 160 C QH min = 7.5 MW 7.5 CP flue gas = = 0.0046 MW/oC 1775 − 145 Fuel req. = 0.0046(1800 − 10) = 8.23 MW Stack loss = 0.0046(170 − 10) = 0.74 MW QH min 7.5 Furnace Eff. = × 100 = × 100 = 91% Fuel req. 8.23
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Combined Heat and Power (Cogeneration)
Combined Heat and Power (Cogeneration)
Heat engine exhaust can be integrated either across or not across the pinch
Heat engine exhaust can be integrated either across or not across the pinch
The process still requires QH min and the heat engine performs NO better than operated stand-alone
Net effect is the import of extra energy W from heat source to produce W power
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Steam Turbine Expansion
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Steam Turbine Integration
Turbine Isentropic Efficiency η T =
actual work H 1 − H 2 = ideal work H 1 − H 2
QFUEL = Q HP + QLP + W + QLOSS
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Gas Turbine Integration
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Combined Heat and Power Schemes: Example The stream data for a heat recovery problem are given below. A problem table analysis for ∆T min = 20oC is also given. The process also has a requirement for 7 MW of power. Two alternative combined heat and power schemes are to be compared economically. Stream No.
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1. A steam turbine with its exhaust saturated at 150oC used for process heating. Superheated steam is generated in the central boilerhouse at 41 bar with a temperature of 300oC. This superheated steam can be expanded in a singlestage turbine with an isentropic efficiency of 85%. Calculate the maximum generation of shaftwork possible by matching the exhaust steam against the process. 2. A second possible scheme uses a gas turbine with a flow rate of air of 97kgs−1 which has an exhaust temperature of 400 oC. Calculate the shaftwork generation if the turbine has an efficiency of 30%. Ambient temperature is 10oC. 3. The cost of heat from fuel for the gas turbine is $4.5GW−1. The cost of imported electricity is $19.2GW−1. Electricity can be exported with a value of $14.4GW−1. The cost for fuel for steam generation is $3.2GW−1. The overall efficiency of steam generation and distribution is 60%. Which scheme is most cost-effective, the steam turbine or the gas turbine ?
Combined Heat and Power Schemes: Example The problem table cascade fo a process is given for ∆T min = 10oC. It is proposed to provide process cooling by steam generation from boiler feedwater with a temperature of 100oC. 1. Determine how much steam can be generated at a saturation temperature of 230 oC. 2. Determine how much steam can be generated at a saturation temperature of 230oC and superheated to the maximum temperature possible against the process. 3. Calculate how much power can be generated from the superheated steam from Part (2), assuming a single-stage condensing steam turbine is to be used with an isentropic efficiency of 85%. Cooling water is available at 20oC and is returned to the cooling tower at 30 oC.
Interval T (oC)
Heat flow (MW)
495
3.6
455 415 305
9.2 10.8 4.2
285 215 195
0.0 16.8 17.6
185 125 95
16.6 16.6 21.1
85
18.1
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Solution (1): Heat available fr steam generation at 235oC interval temperature is 12.0 MW Latent heat of water a sat. temp. of 235 oC is 1812 kJ · kg−1K−1 3
Steam = 12.0 × 10 = 6.62 kg · s−1 Prod. 1812 Taking the heat capacity of water to be 4.3 kJ · kg−1K−1, heat duty on boiler feedwater preheating = 6.62 × 4.3 × 10−3(230 − 100) = 3.70 MW The process can support both boiler feedwater preheat and steam generation.
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Turbine outlet conditions for isentropic expansion to 40 oC from steam tables are: P 2 = 0.074 bar. For S 2 = 6.488 kJ · kg−1 K−1, the wetness fraction (X ) and outlet enthalpy H 2 can be calculated (?)
Solution (2,3): Maximum superheat temp.: = 285oC interval = 280oC actual Heat available for steam generation at 235oC interval temperature is 12.0 MW. From steam table, enthalpy of superheated steam at 280oC and 28 bar is 2947 kJ · kg−1 ,
X = 0.23,
H 2 = 2020kJ · kg−1
For a single-stage expansion with isentropic efficiency of 85%: H 2 = 2947 − 0.85(2947 − 2020) = 2159kJ · kg−1 The power generation (W ) is given by
and enthalpy of saturated water at 230 oC and 28 bar is 991 kJ · kg−1 W = 6.13(2947 − 2159) × 10−3 = 4.8 MW
The wetness fraction for the real expansion is given by
The lowest condensing temp is cooling water temp plus ∆T min = 30 + 10 = 40oC. From steam table, inlet condition at T 1 = 280oC and P 1 = 28 bar are: H 1 = 2947 kJ · kg−1 ;
H 2 = 2159 = X H + (1 − X )H v = 167.5X + 2574(1 − X ) = 0.17 ⇒ X
S 1 = 6.488 kJ · kg−1K−1
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Heat Pump and Power Cycle
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Integration of Heat Pumps Schematic of a simple vapor compression heat pump
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Integration of Heat Pumps
Integration of Heat Pumps
Schematic of a simple vapor compression heat pump (again)
Schematic of a simple vapor compression heat pump (again)
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Integration of Heat Pumps
Integration of Heat Pumps
Schematic of a simple vapor compression heat pump (again)
Schematic of a simple vapor compression heat pump (again)
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Integration of Heat Pumps
Integration of Heat Pumps
Schematic of a simple vapor compression heat pump (again)
Integration of a heat pump above the pinch
The system converts power into heat !!
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Integration of Heat Pumps
Integration of Heat Pumps
Integration of a heat pump below the pinch
Integration of a heat pump across the pinch
Power is turned into waste heat !!
Heat is pumped from a heat source part to a heat sink part Coefficient QHP + W COPHP = of W Performance
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Integration of Heat Pumps
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Integration of Heat Pumps
The grand composite curve
The grand composite curve allows heat pump cycles to be sized
A temperature lift greater than 25oC is rarely economic
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Integration of Heat Pumps
Integration of Heat Pumps
Little scope for heat pumping across process pinch
Heat pump placed across a utility pinch
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The
Grand Composite Curve allows selection of utility mix for individual processes
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Thank You for Your Attention Questions Are Welcome