Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F22—STEAM GENERATION
  • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
  • F22B29/00—Steam boilers of forced-flow type
  • F22B29/06—Steam boilers of forced-flow type of once-through type, i.e. built-up from tubes receiving water at one end and delivering superheated steam at the other end of the tubes
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F22—STEAM GENERATION
  • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
  • F22B29/00—Steam boilers of forced-flow type
  • F22B29/06—Steam boilers of forced-flow type of once-through type, i.e. built-up from tubes receiving water at one end and delivering superheated steam at the other end of the tubes
  • F22B29/067—Steam boilers of forced-flow type of once-through type, i.e. built-up from tubes receiving water at one end and delivering superheated steam at the other end of the tubes operating at critical or supercritical pressure

Definitions

• the invention relates to a once-through steam generator with a combustion chamber surrounded by a surrounding wall of pipes which are connected to one another in a gas-tight manner, wherein the pipes which run vertically and have a surface structure on the inside thereof can be cut by a flow medium from bottom to top.
• Such a steam generator is known from the article "Evaporator Concepts for Benson Steam Generators” by J. Franke, W. Köhler and E. Wittchow, published in VGB Kraftwerkstechnik 73 (1993), Issue 4, pp. 352 to 360
• Such a continuous steam generator leads to the heating of the combustion chamber forming evaporator tubes, in contrast to a natural circulation or forced circulation steam generator with only partial evaporation of the water / water / steam mixture circulated, to a complete evaporation of the
• Flow medium in the evaporator tubes in one pass While in the natural circulation steam generator the evaporator tubes are in principle arranged vertically, the evaporator tubes of the continuous steam generator can be arranged both vertically and spirally - and thus inclined.
• a continuous steam generator the combustion chamber walls of which is constructed from vertically arranged evaporator tubes, is less expensive to manufacture than a continuous steam generator having a spiral-shaped tube.
• Continuous-flow steam generators with vertical pipes also have lower water / steam-side pressure losses than those with inclined or spirally rising evaporator pipes.
• a particular problem is the design of the combustion chamber or peripheral wall of the once-through steam generator with regard to the pipe wall or material temperatures that occur there.
• the temperature of the combustion chamber wall is essentially determined by the level of the saturation temperature of the water if wetting of the heating surface in the evaporation area can be ensured. This will e.g. achieved by using inner finned tubes.
• Such pipes and their use in steam generators are e.g. B. is known from European patent application 0 503 116. These so-called finned tubes, d. H. Pipes with a ribbed inner surface have a particularly good heat transfer from the inner wall to the flow medium.
• the invention is based on the object of specifying a design criterion suitable for a particularly favorable mass flow density in the pipes for pipes of a peripheral wall of a once-through steam generator.
• ⁇ T w (K) is the temperature difference between the outer and inner wall of the tube, and C ⁇ 7.3 * 10 "3 kWs / kgK is a constant.
• the invention is based on the consideration that for the fluidic design of the internally finned pipes because the mass flow density had to meet two fundamentally contradictory conditions.
• the average mass flow density in the pipes should be chosen to be as low as possible. This is to ensure that a higher mass flow flows through individual pipes, to which more heat is supplied than other pipes due to unavoidable differences in heating, than pipes which are heated on average.
• This natural circulation characteristic known from the drum boiler leads to an equalization of the steam temperature and thus the pipe wall temperatures at the outlet of the evaporator heating surface.
• the mass flow density in the pipes must be chosen so high that reliable cooling of the pipe wall is ensured and permissible material temperatures are not exceeded. In this way, high local overheating of the pipe material and the associated damage (pipe ripper) are avoided.
• the main influencing variables for the material temperature are the external heating of the pipe wall and the heat transfer from the inner pipe wall to the flow medium (fluid). There is thus a connection between the internal heat transfer, which is influenced by the mass flow density, and the external heating of the tube wall.
• Step 2
• T max Maximum material temperature (° C) T kri t Temperature of the fluid at the critical point (° C) ß Thermal expansion coefficient (1 / K) E modulus of elasticity (N / mm 2 )
• Tmax Tkrit + 6 'Gml (° C) (3)
• the permissible voltage can be found in the pipe manufacturer's specifications.
• Step 3 Conversion of the specified heat flow density q a (related to the outside of the pipe wall) to a heat flow density q i ( related to the inner wall of the pipes:
• FIG. 1 shows a simplified representation of a continuous steam generator with vertically arranged evaporator tubes
• FIG. 2 shows a single evaporator tube in cross section
• FIG. 3 shows curves E, F, G and H for the mass flow density in the case of various geometries of an evaporator tube made of the material 13 Cr Mo 44, and
• Figure 4 is a graphical representation of the dependence of the maximum permissible material temperature of 13 CrMo 44 on the permissible stress (N / mm 2 ).
• a continuous steam generator 2 is shown schematically with a rectangular cross section, the vertical gas train is formed from a surrounding wall 4, which merges into a funnel-shaped bottom 6 at the lower end.
• the bottom 6 comprises a discharge opening 8 for ashes, not shown.
• a number of burners 10, only one of which is visible, are attached for a fossil fuel in the surrounding wall or combustion chamber 4 formed from vertically arranged evaporator tubes 12.
• the vertically arranged evaporator tubes 12 are welded together in this area A via tube fins or tube webs 14 to form gas-tight combustion chamber or peripheral walls.
• the evaporator tubes 12 flowed through from bottom to top during operation of the continuous-flow steam generator 2 form an evaporator heating surface 16 in this area A.
• the continuous steam generator 2 when the continuous steam generator 2 is operating, there is a flame body 17 which arises when a fossil fuel is burned, so that this region A of the continuous steam generator 2 is distinguished by a very high heat flow density.
• the flame body 17 has a temperature profile which, starting from approximately the center of the combustion chamber 4, decreases both in the vertical direction upwards and downwards and in the horizontal direction to the sides, ie to the corners of the combustion chamber 4.
• Above the lower area A of the throttle cable there is a second area B remote from the flame, above which a third upper area C of the throttle cable is provided.
• Convection heating surfaces 18, 20 and 22 are arranged in areas B and C of the gas flue.
• FIG. 2 shows an evaporator tube 12 provided on the inside with ribs 26, which during operation of the continuous steam generator 2 on the outside inside the combustion chamber 4 is exposed to heating with the heat flow density q a and through which the flow medium S flows on the inside.
• T k the temperature of the flow medium or fluid in the tube 12 is designated T k ⁇ t.
• Omax the maximum permissible material temperature T ⁇ x at the pipe apex 28 of the heated side of the pipe wall is used.
• the inner diameter and the outer diameter of the evaporator tube 12 are denoted by d x and d a , respectively.
• the equivalent inner diameter must be used, which takes into account the influence of the fin heights and valleys.
• the pipe wall thickness is denoted by d r .
• FIG. 3 shows four curves E, F, G and H in a coordinate system for different outside diameters d a (mm) and tube wall thicknesses d r (mm).
• the heat flow density q a (kW / m 2 ) is plotted on the outside of the pipe and the preferred or optimal mass flow density rh (kg / m 2 s) is plotted on the ordinate.
• Curve E shows the course for a pipe outer diameter d a of 30 mm with a pipe wall thickness d r of 7 mm.
• Curve F shows the course for a pipe outer diameter d a of 40 mm with a pipe wall thickness d r of 7 mm.
• Curve G shows the course of the mass flow density m as a function of the heat flow density q a for a pipe 12 with an outer diameter d a of 30 mm and a pipe wall thickness d r of 6 mm.
• Curve H shows the course of a tube 12 with an outer diameter d a of 40 mm and a tube wall thickness d r of 6 mm.
• the mass flow densities m are calculated for heat flow densities q a of 250, 300, 350 and 400 kW / m 2 at critical pressure of the flow medium S for the tube material 13 CrMo 44.
• An example for the determination of the optimal mass flow density th is shown below. The following conditions are required:
• di 26 mm inner tube diameter.
• Step 1 Calculation of the heat flow density
• the heat flow density based on the thermal calculation is multiplied by the increase factor. It follows:
• Step 2 Determining the maximum permissible material temperature
• Step 3 heat flow density on the inside of the pipe
• the optimal mass flow density rh can thus be determined. This value is represented by the dashed lines in FIG. 3 for the specified conditions. It can be seen that for the assumed heat flow density q a of the pipe outer side of 350 kW / m 2 for pipes 12 with outer diameters d a between 30 and 40 mm and wall thicknesses d r between 6 and 7 mm there are optimal mass flow densities rh between 740 and 1060 kg / m 2 s result.
• the mass flow rate determined in this way can be used for the fluidic design of the tubes 12 of the tube or peripheral wall 4.
• dense rh can still be converted to the conditions at 100% load.
• the operating pressure at the inlet of the tubes 12 is calculated at 100 Z.

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• Engineering & Computer Science (AREA)
• Physics & Mathematics (AREA)
• Thermal Sciences (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
• Control Of Steam Boilers And Waste-Gas Boilers (AREA)
• Rigid Pipes And Flexible Pipes (AREA)
• Treatment Of Fiber Materials (AREA)
• Fluidized-Bed Combustion And Resonant Combustion (AREA)

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• 1996
  • 1996-01-25 DE DE19602680A patent/DE19602680C2/de not_active Expired - Fee Related
• 1997
  • 1997-01-14 RU RU98115910/06A patent/RU2175095C2/ru active
  • 1997-01-14 KR KR1019980705679A patent/KR19990081961A/ko not_active Application Discontinuation
  • 1997-01-14 WO PCT/DE1997/000049 patent/WO1997027426A2/de not_active Application Discontinuation
  • 1997-01-14 CN CN97191903A patent/CN1209868A/zh active Pending
  • 1997-01-14 EP EP97915255A patent/EP0876569A2/de not_active Ceased
  • 1997-01-14 JP JP9526408A patent/JP2000503382A/ja active Pending
• 1998
  • 1998-07-27 US US09/123,102 patent/US5967097A/en not_active Expired - Fee Related

Non-Patent Citations (1)

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