Boiling Process
Boiling Process
When thermal energy is applied to furnace tubes, the process of boiling is initiated. The fluid leaving the furnace tubes and going back to the steam drum is not 100% steam but is
a mixture of water and steam. The ratio of the mixture flow to steam generated is known as the circulation ratio (CR). Typically, the steam quality in the furnace tubes is 5%–8%, which means that the mixture is mostly water with CR ranging from 20 to 12. As discussed later in natural circulation units, CR depends on the resistance of the various circuits and energy absorbed in each of them. In a D-type boiler, for example, the convection bank tubes and side walls have shorter tubes, while the side wall forming the D has a much longer length, and hence, the CR will be different in each parallel path.
Nucleate boiling is the process preferred in boilers. In this process, the steam bubbles generated by the energy input are removed by the mixture at the same rate so that the tubes are kept cool. The steam bubbles are contained within the water film, which keeps the tube inner surface wet and hence cool. Boiling heat transfer coefficients are very high on the
order of 25,000–40,000 W/m 2 K (about 7,900–12,650 Btu/ft 2 h °F) as shown earlier. When the intensity of heat flux exceeds a value known as the CHF, then the process of nucleate boiling is disrupted. The bubbles formed inside the tubes are not removed adequately by the mixture flowing inside. The bubble formation interferes with the flow of mixture and forms a superheated steam film inside the tubes, which has a lower heat transfer coefficient and hence can increase the tube wall temperatures significantly as shown in Figure 2.12. It is the boiler designer’s job to ensure that heat fluxes are kept within limits.
Generally, heat fluxes in package boilers are quite small compared to utility boilers as the furnace sizes are quite large relative to the energy input. Besides, they operate at much lower pressures, and hence, rarely does one hear of tube failures due to high heat flux or an associated problem called DNB. The actual heat fluxes in package boilers range from 126
to 222 kW/m 2 (40,000–70,000 Btu/ft 2 h), while CHF levels could be in excess of 790 kW/m 2 (250,000 Btu/ft 2 h) at the CR and steam pressures seen in package boilers. Rifled tubes are used in high-pressure boilers to ensure that tube inner surfaces are wetted by the water film. They have spiral grooves cut into their inner wall surface. The swirl flow induced by
70 Steam Generators and Waste Heat Boilers: For Process and Plant Engineers
Steam–water mixture
Film boiling
Heat
Transition boiling
DNB
Nucleate boiling
Tube metal temperature Water
FIGURE 2.12
Boiling process and DNB in boiler tubes. the rifled tubes not only forces more water outward on to the wall surfaces but also pro-
motes mixing between the phases to counteract the gravitational stratification effects in
a nonvertical tube. Horizontal tubes have a lower limit for CHF values as stratification of flow is a possibility compared to vertical tubes. Rifled tubes can handle a much higher heat flux about 50% more than plain tubes. As they are expensive, large utility high-pressure steam generators use them in high heat flux areas only.
At DNB conditions, the bubbles of steam forming on the hot tube surface begin to inter- fere with the flow of water to the tube surface and eventually coalesce to form a film of steam that blankets the hot tube inner surface. The transition from nucleate boiling to steady-state film boiling is unstable because of the sweeping away of the coalescing bub- bles. As this unsteady transition approaches full film boiling, the tube wall temperature fluctuates significantly, and large temperature increases on the order of 30°C–60°C are seen as shown in Figure 2.12.
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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