Hot Casing Design
Hot Casing Design
Whenever hot gases are contained in an internally refractory-lined (or insulated) duct, the casing temperature can fall below the acid dew point in cold weather. The hot gases can seep through the refractory cracks over a period of time and can cause acid condensation with its associated problems. Some engineers prefer what is called a hot casing whereby the duct casing is made hot (above the acid dew point) by externally insulating the duct (Figure 6.5). This lowers the heat losses also. However, if calculations are not properly done and a thicker-than-required external insulation is used, the duct temperature can be made significantly hot and can cause expansion problems. If the gas temperature varies along the gas path (say, a boiler), then higher thicknesses have to be applied externally as the gas tem- perature reduces in order to keep the casing temperature within a range of temperature.
Example 6.9
A waste heat boiler has a gas inlet temperature of 704°C and cools to 250°C. The cas- ing has 125 mm of Greencast 22 refractory followed by 50 mm of castable block mix refractory. The casing temperature based on 27°C ambient and zero wind velocity is estimated as 78°C as shown later. Since this is below the sulfuric acid dew point tem- perature of 120°C, external insulation should be applied to raise the casing temperature. The results from a computer program are shown in Table 6.3 for various cases. Let the acid dew point be 130 °C. (For simplicity and to illustrate the point, gas temperature is assumed to be the hot face temperature.)
In case 1, the hot gases are contained in a refractory-lined casing. The hot layer of refractory is Castolite 22. K ranges from 0.245 to 0.324 W/m K from 200°C to 871°C. Refractory 2 is castable block mix, and K ranges from 0.082 to 0.121 W/m K from 93°C to 427°C. Mineral fiber insulation K ranges from 0.052 to 0.095 W/m K from 93°C to 427°C.
Hot casing arrangement.
Miscellaneous Boiler Calculations 323
TABLE 6.3
Summary of Refractory Calculations
Case 3 Case 4 Layer
Case 1
Case 2
Temp. In–Out
Temp. In–Out
Temp. In–Out Temp. In–Out
250°C–196°C 250°C–176°C Refractory 2
Refractory 1
700°C–411°C
700°C–459°C
196°C–134°C 176°C–89°C Min fiber
411°C–78°C
459°C–204°C
204°C–72°C
134°C–38°C 89°C–42°C
0.150 Fiber thickness, mm
Heat loss, kW/m 2 0.640
0 12 38 12 Note: Refractory 1: Castolite 22. Refractory 2: Castable block mix.
TABLE 6.4
Heat Loss Equation
SI Units British Units
q = 5.67 × 10 −11 × ∈ (T s 4 − T a 4 ) + 0.00195(T s −T a ) 1.25 ×
Q = 0.1714 × 10 −8 × ∈ (T s 4 −T a 4 ) + 0.296(T s −T a ) 1.25 ×
{(V + 21)/21} 0.5 {(V + 69)/69) 0.5 q is the heat loss, kW/m 2 Btu/ft 2 h
T s is the hot face temperature, K
°R
T a is the cold face temperature, K
°R
V is the wind velocity, m/min
ft/min
∈ is the emissivity
∈ is the emissivity
It can be seen that when we have only the two layers of refractory inside the casing, the casing temperature drops to 78°C. This may cause water and acid condensation if some flue gases seep through the refractory. When we add 12 mm insulation outside the casing, the casing temperature increases to 204°C, and heat loss is kept low as the casing temperature of the insulation is only 72°C. Thus, casing corrosion concerns are minimized. As the gas cools, we note that we have to use a higher external insulation thickness to keep the casing hot. If we use say 12 mm thick insulation when the gases are at 250°C (case 4), the casing temperature drops to 89°C and below the acid dew point temperature. If we use a higher thickness of 38 mm (case 3), the casing temperature increases to 134°C while the heat loss is also minimized.
The other option of minimizing corrosion is to use membrane wall casing; in this case, the tube wall temperature is close to the saturation steam temperature and always above the dew point. External mineral fiber insulation of say 50–75 mm will be adequate. The choice is left to the boiler supplier. Membrane wall casing may be more expensive for some boiler suppliers.
Table 6.4 shows the heat loss equations in both SI and British units.
Parts
» For Process and Plant Engineers
» A Few Typical Solved Problems
» Excess Air from Flue Gas Analysis
» Simplified Combustion Calculations
» Relating Oxygen and Energy Input in Turbine Exhaust Gases
» Evaluating Fuel Quantity Required to Raise Turbine Exhaust Gas Temperature
» Simplified Formulae for Boiler Efficiency
» Firing Fuels with Low Heating Values
» Boiler duty and efficiency calculations
» Acid Dew Point Temperature T dp
» Steam Generator Furnace Design
» Advantages of Water-Cooled Furnaces
» Furnace Exit Gas Temperature Evaluation
» Empirical Formula for Furnace Duty Estimation
» Distribution of Radiation to Tube Banks
» External Radiation to Heat Transfer Surfaces at Furnace Exit
» Correlations for CHF (Critical Heat Flux) and Allowable Steam Quality
» Guidelines for Good Circulation System Design
» Emissions Affect Steam Generator Designs
» Adding Condensate Heater to Improve Boiler Plant Efficiency
» Understanding Boiler Surface Areas
» Steam Generators for Oil Sands Application
» Radiant versus Convective Superheaters
» Steam Inlet and Exit Nozzle Location
» Case Study of a Superheater with Tube Failure Problems
» Problem at Low Loads with Inverted-Loop Superheaters
» Data Required for Performing Steam Generator Analysis
» Evaluating Part Load Performance
» Tube Wall Temperature Estimation at Economizer Inlet
» Methods to Minimize Low-Temperature Corrosion Problems
» Water Chemistry, Carryover, Steam Purity
» Sizing and Performance Calculations
» Flue Gas Composition and Gas Pressure
» Heat Recovery in Sulfur Plants
» Heat Recovery in Sulfuric Acid Plant
» Heat Recovery in Hydrogen Plants
» Combining Solar Energy with Heat Recovery Systems
» Natural versus Forced Circulation HRSGs
» Optimizing Pinch and Approach Points in HRSGs
» HRSG Performance and Evaluating Field Data
» Advantages of Supplementary Firing in HRSGs
» Performance with and without Export Steam
» Cement Plant Waste Heat Recovery
» Fluid Heaters and Film Temperature
» Boiling Heat Transfer Coefficient h o
» Off-Design Performance with Addition of Economizer
» Simulation of Fire Tube Boiler Performance
» Simplified Approach to Evaluating Performance of Fire Tube Boilers
» Heat Transfer Inside and Outside Tubes
» Specifying Waste Heat Boilers
» Understanding Pinch and Approach Points
» Estimating Steam Generation and Gas–Steam Temperature Profiles
» Why Cannot We Arbitrarily Select the Pinch and Approach Points?
» Off-Design Performance Evaluation
» Single- or Multiple-Pressure HRSG
» Cogeneration Plant Application
» Water Dew Point of Flue Gases
» Condensation Heat Transfer Calculations
» Condensation over Finned Tubes
» Drum Coil Heater: Bath Heater Sizing
» Checking Heat Transfer Equipment for Noise and Vibration Problems
» Steam Drum Calculations Steam Velocity in Drum
» Flow Instability in Two-Phase Circuits
» Superheater Design and Off-Design Calculation
» NTU Method of Performance Evaluation (Number of Transfer Units)
» Appendix B: Tube-Side Heat Transfer Coefficients and Pressure Drop
» Another Method of Estimating h c for Water
» Importance of Streams in Superheater, Economizer
» Simplified Procedure for Evaluating Performance of Plain Tube Bundles
» Appendix D: Nonluminous Heat Transfer Calculations
» Determination of Heat Transfer Coefficient h c Convective Heat Transfer Coefficient
» How Is Life of Superheater Affected by High Tube Wall Temperatures?
» Effect of h i on Fin Selection
» Reduce Weight of Tube Bundles Using Smaller Tubes
» Effect of Outside Fouling Factor
» Effect of Fin Thickness and Conductivity
» Why Are Fins Not Used in Gas–Gas Exchangers?
» Appendix F: Properties of Gases
» Flue Gas Mixture Properties Calculation
» Appendix G: Quiz on Boilers and HRSGs with Answers
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