EP0439765B1 - Dampferzeuger - Google Patents

Dampferzeuger Download PDF

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Publication number
EP0439765B1
EP0439765B1 EP90124271A EP90124271A EP0439765B1 EP 0439765 B1 EP0439765 B1 EP 0439765B1 EP 90124271 A EP90124271 A EP 90124271A EP 90124271 A EP90124271 A EP 90124271A EP 0439765 B1 EP0439765 B1 EP 0439765B1
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EP
European Patent Office
Prior art keywords
steam
steam generator
tube wall
line
gas
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP90124271A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0439765A1 (de
Inventor
Eberhard Dipl.-Ing. Wittchow
Joachim Dr. Franke
Wolfgang Dipl.-Ing. Vollmer
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Siemens AG
Original Assignee
Siemens AG
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Filing date
Publication date
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Publication of EP0439765A1 publication Critical patent/EP0439765A1/de
Application granted granted Critical
Publication of EP0439765B1 publication Critical patent/EP0439765B1/de
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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
    • F22B29/02—Steam boilers of forced-flow type of forced-circulation type
    • F22B29/023—Steam boilers of forced-flow type of forced-circulation type without drums, i.e. without hot water storage in the boiler
    • F22B29/026—Steam boilers of forced-flow type of forced-circulation type without drums, i.e. without hot water storage in the boiler operating at critical or supercritical pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B35/00—Control systems for steam boilers
    • F22B35/02—Control systems for steam boilers for steam boilers with natural convection circulation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B35/00—Control systems for steam boilers
    • F22B35/06—Control systems for steam boilers for steam boilers of forced-flow type
    • F22B35/08—Control systems for steam boilers for steam boilers of forced-flow type of forced-circulation type
    • F22B35/083—Control systems for steam boilers for steam boilers of forced-flow type of forced-circulation type without drum, i.e. without hot water storage in the boiler
    • F22B35/086—Control systems for steam boilers for steam boilers of forced-flow type of forced-circulation type without drum, i.e. without hot water storage in the boiler operating at critical or supercritical pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B37/00—Component parts or details of steam boilers
    • F22B37/02—Component parts or details of steam boilers applicable to more than one kind or type of steam boiler
    • F22B37/10—Water tubes; Accessories therefor
    • F22B37/14—Supply mains, e.g. rising mains, down-comers, in connection with water tubes
    • F22B37/141—Supply mains, e.g. rising mains, down-comers, in connection with water tubes involving vertically-disposed water tubes, e.g. walls built-up from vertical tubes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22D—PREHEATING, OR ACCUMULATING PREHEATED, FEED-WATER FOR STEAM GENERATION; FEED-WATER SUPPLY FOR STEAM GENERATION; CONTROLLING WATER LEVEL FOR STEAM GENERATION; AUXILIARY DEVICES FOR PROMOTING WATER CIRCULATION WITHIN STEAM BOILERS
    • F22D5/00—Controlling water feed or water level; Automatic water feeding or water-level regulators
    • F22D5/26—Automatic feed-control systems

Definitions

  • a downpipe is located outside of the throttle cable and connects a mixing chamber to the inlet header.
  • a feed water line which has an economizer, and a pipeline are connected to this mixing chamber.
  • this pipeline there is a circulating pump which blocks the circulation in the downpipe when stationary and which is connected to the flow on the suction side with the outlet header and on the pressure side via a valve with the mixing chamber.
  • a pipe leads from the outlet manifold to several secondary heating surfaces connected in series.
  • a control device influences the feed water flow into the economizer, which is located in the feed water line, via a valve.
  • This control device records the steam temperature and steam pressure in the connecting line between the last reheating surface and a steam turbine as a control variable.
  • the known steam generator is operated at supercritical pressure, and the circulation pump connected on the suction side to the outlet header and on the pressure side via the valve to the mixing chamber therefore only conveys the single-phase medium which arises at supercritical pressure in the outlet header.
  • this circulation pump cannot convey a two-phase medium, since it would be destroyed by cavitation in a very short time, so that operation of the steam generator at subcritical pressure and thus sliding pressure operation of this steam generator is not possible.
  • the invention has for its object to enable sliding pressure operation of the steam generator.
  • the control device which records one of the control variables a) to e), remains functional not only at subcritical but also at critical and supercritical pressure in the steam generator and thus in the entire sliding pressure range of the steam generator, while the control device, which records control variable f), does can only be operated as long as the pressure in the steam generator is below the critical pressure, but can react very quickly to changes in the heat output that is transferred to the water evaporating in the steam generator.
  • load changes in the steam generator automatically lead to changes in the length of the heating surface available for overheating the generated steam, since the end of evaporation of the water is not retained by the water level in the outlet collector, and the temperature of the steam leaving the post-heating surfaces remains constant despite changes in load .
  • control is carried out on at least one of the control variables a) to f), that is to say no water level control is carried out on the outlet header.
  • the downpipe of the steam generator enables circulation through the pipes of the gas-tight pipe wall even without a forced pump in the downpipe, regardless of whether there is subcritical, critical or supercritical pressure in the steam generator.
  • This circulation can bring about a high mass flow in the pipes of the gas-tight pipe wall and thus good cooling of these pipes even if only a relatively small feed water flow is fed to the steam generator. Therefore, the steam generator can be designed for relatively low steam outputs be, which is an advantage, for example, in environmentally friendly thermal power stations.
  • the formation of the steam generator according to the invention results in a quickly responsive and particularly accurate control of the feed water flow in the feed water line.
  • the tubes of the gas-tight tube wall of the steam generator can be arranged vertically, so that the steam generator can be manufactured particularly inexpensively.
  • the circulation through these vertically arranged tubes of the tube wall can even be a natural circulation due to the optimally low flow resistance in the tubes.
  • the claims 4 to 12 and 16 are directed to advantageous developments with which a high circulation through the downpipe and the tubes of the gas-tight tube wall is generated even at high pressure, especially at supercritical pressure in the steam generator.
  • Claim 13 is directed to a training that the Starting the steam generator is easier.
  • the further subclaims 14 and 15 deal with superimposed and / or superseding regulations.
  • the vertical throttle cable according to FIG. 1 with a rectangular cross section is formed by a gas-tight tube wall 2 which merges into a base 3 in the form of a funnel at the lower end of the gas cable.
  • the tubes 4 run in the longitudinal sectional planes of the throttle cable, otherwise the tubes 4 of the tube wall 2 are arranged vertically.
  • all tubes 4 of the tube wall 2 and the base 3 are welded together gas-tight on their long sides.
  • the bottom 3 forms a discharge opening for ashes, not shown.
  • tubes 4 of tube wall 2 are curved and run on the outside of the vertical throttle cable. Similar openings can also be formed for air nozzles, flue gas nozzles, soot blowers, etc.
  • the pipes 4 of the pipe wall 2 are connected to inlet collectors 6 with their inlet ends formed by their lower ends and to outlet collectors 7 with their outlet ends formed by their upper ends.
  • the outlet manifold 7 and the inlet manifold 6 are located outside the throttle cable.
  • the outlet manifolds 7 have a locally higher level than the inlet manifolds 6.
  • each outlet manifold 7 with vertical downspouts 8, which are also located outside the throttle cable, is connected in terms of flow to the inlet manifold 6, to which the tubes 4 of the tube wall 2 are also connected, which open into this outlet collector 7.
  • a feed water line 47 which contains an economizer (feed water preheater) 48, leads into the outlet header 7.
  • This economizer 48 is formed by an inlet header, an outlet header and heating surface tubes connecting these two collectors in terms of flow, which are not shown in FIG. 1 and are arranged as a heating surface within a gas flue, which adjoins the gas line according to FIG. 1 at its upper end.
  • a control valve 9 with a motor drive 10 is located in front of the economizer 48 in the feed water line 47.
  • a steam line 11 which contains two post-heating surfaces 12 and 13 connected in series and a water separator 14 connected between these two post-heating surfaces 12 and 13.
  • the outlet header 7, the steam line 11, the reheating surfaces 12 and 13 and the water separator 14 are thus connected to one another in terms of flow and connected in series.
  • the post-heating surfaces 12 and 13 not shown in FIG. 1 have heating surface tubes with inlet and outlet headers and are arranged within the throttle cable which adjoins the throttle cable according to FIG. 1 at its upper end.
  • the outlet header 7 is provided with a level indicator 21 (e.g. float) for measuring the water level in the outlet header 7.
  • a level indicator 21 e.g. float
  • the post-heating surface 12 immediately downstream of the outlet header 7 in the steam line 11 has a device 22 (e.g. thermocouple) at its outlet end, which measures either the steam temperature at this outlet end or the material temperature corresponding to this steam temperature at this outlet end. Furthermore, this outlet end of the reheating surface 12 is provided with a device 23 (e.g. spring pressure meter as pressure transmitter) for measuring the vapor pressure at this outlet end.
  • a device 22 e.g. thermocouple
  • feed water flow meter 24 feed water quantity per unit of time which is connected upstream of the economizer 48 and downstream of the control valve 9.
  • Control valve 9 with motor drive 10, device 22 for measuring the steam temperature or a material temperature corresponding to the steam temperature and device 23 for measuring the steam pressure and feed water flow meter 24 are part of a control device of the steam generator for influencing the feed water flow into the steam generator.
  • This control device also has a transmitter 25 (signal converter) for the device 22 for measuring the steam temperature or a material temperature corresponding to the steam temperature, a measuring transducer 26 for the device 23 for measuring the steam pressure and a measuring transducer 27 for the feed water flow meter 24.
  • the transducers 25 and 26 each output an output signal to a device 28 having a computer for determining the steam enthalpy from the quantities of steam temperature and steam pressure, which the devices 22 and 23 measure.
  • the device 28 for determining the enthalpy of vapor in turn outputs a signal at its output to a controller 29 which is provided with a setpoint adjuster 30.
  • the output signal of the controller 29 and the output signal of a setpoint adjuster 35 are fed to a maximum value selection device 36, the output signal of which is fed to a controller 37.
  • the output signal of the transmitter 27 is also fed to the controller 37.
  • the water separator 14 is provided with a level gauge 31 for measuring the water level in the water separator 14.
  • An output signal is led from a measuring transducer 32 of the level indicator 31 to a controller 33, which is provided with a set point adjuster 34 and which acts on the motor drive 17 of the sequence control valve 16.
  • the feed water line 47 with the economizer 48, the inlet header 6, the tubes 4 of the tube wall 2 and the downpipes 8 are filled with feed water until the burner 7 in the openings 99 according to FIG a water level is measured with the level indicator 21.
  • the setpoint adjuster 35 specifies a specific setpoint for the feedwater flow measured with the feedwater flow meter 24, which acts on the controller 37 via the maximum value selection device 36 and sets the feedwater flow to the outlet header 7 via the motor drive 10 via the motor drive 10.
  • the controller 29 is switched on by hand, for example, so that it supplies an output signal led to the maximum value selection device 36.
  • the output signal of the controller 29 as the set point for the feed water flow, which is measured by the feed water flow meter 24, is very low.
  • the maximum value selection device 36 therefore continues to select the output signal of the setpoint adjuster 35 for influencing the feed water supply, which output signal is greater than the output signal of the controller 29.
  • the steam pressure in the steam generator is usually still below the critical pressure.
  • the steam pressure is then subsequently increased to the extent required by the steam turbine of the power plant fed by the steam generator.
  • the steam generator is operated at critical or supercritical pressure. Nevertheless, the natural circulation through the pipes 4 of the pipe wall 2 and the down pipes 8 is maintained, and the feed water supply through the feed water line 47 can be regulated to a steam enthalpy in the steam line 11 which is predetermined by the setpoint adjuster 30. Because of the natural circulation in the pipes 4 and in the down pipes 8, the steam generator can even be supplied with a relatively low feed water flow without the cooling of the pipes 4 of the pipe wall 2 being endangered.
  • While regulating the feed water supply through the feed water line 47 to a predetermined steam enthalpy according to FIG. 2 is advantageous when operating the steam generator with load-proportional steam pressure (sliding pressure operation), it may be sufficient, for example, when the steam generator is operated with constant steam pressure (fixed pressure operation) if the output signal of the transmitter is sufficient 25 in FIG. 2, which is assigned to the device 22 for measuring the steam temperature, is connected directly to the controller 29 and the device 23 for measuring the steam pressure with the transmitter 26 and the device 28 for determining the steam enthalpy are eliminated.
  • a setpoint value of the steam temperature at the outlet end of the reheating surface 12 is then specified with the setpoint adjuster 30.
  • the water separator 14 is a control device
  • the steam generator according to FIG. 3 essentially differs from the steam generator according to FIG. 2 in that instead of the devices 22 and 23 for measuring the steam temperature and the steam pressure at the outlet end of the reheating surface 12 on a pipe 4 the tube wall 2, a device 69 for measuring tube wall temperatures is provided on this tube 4.
  • this device 69 essentially has two thermocouples 70 and 71.
  • the pipe 4 in question is provided with a pipe section 4a which is eccentrically thickened in the pipe wall 2, which is shown in cross section in FIG. 4, towards the interior of the throttle cable and which is welded into the pipe wall 2.
  • the eccentrically thickened pipe section 4a is provided in the interior of the throttle cable with two transverse bores 70a and 71a, which are parallel to one another and spaced apart from one another in the radial direction.
  • the thermocouple 70 and 71 are arranged in each of these transverse bores 70a and 71a.
  • the connecting wires of these two thermocouples 70 and 71 are covered by a U-profile 72 which is also welded into the tube wall 2 and are guided onto the outside of the tube wall 2 into a protective tube 73 located there.
  • the thermocouples 70 and 71 for measuring the tube wall temperatures at two different locations on the eccentrically thickened tube section 4a include the transmitters 72 and 73 in FIG. 3. Of these transmitters 72 and 73, an output signal is fed to a device 74 having a computer. This device 74 determines from the temperatures of the eccentrically thickened pipe section 4a measured with the thermocouples 70 and 71 and other variables such as the wall thickness and the thermal resistance of this pipe section 4a the heat output transferred to the evaporating water. Such devices 69 are conveniently attached several times to the pipe wall 2 in order to transfer the thermal power transferred to the evaporating water to several pipes 4 and at different locations to measure this tube wall 2. The accuracy of the measurements can be increased by averaging the measured variables.
  • the heat output determined in this way is multiplied in the device 74 by the surface of the pipe wall 2 on the inside of the throttle cable, so that the output signal from the device 74 is proportional to the heat output transmitted to the entire pipe wall 2.
  • the output signal from the device 74 for determining the thermal output is led to a controller 75, which is provided with a setpoint adjuster 76.
  • the output signals of the controller 75 and a setpoint adjuster 35 are routed to a maximum value selection device 77, the output signal of which is in turn routed to a controller 37.
  • the output signal of a transmitter 27 assigned to the feed water flow meter 24 is also connected to this controller 37, as in FIG.
  • the mode of operation of the controller 75, the setpoint adjuster 76, the maximum value selector 77 and the setpoint adjuster 35 according to FIG. 3 corresponds to the mode of operation of the controller 29, the setpoint adjuster 30, the maximum value selector 36 and the setpoint adjuster 35 of the steam generator according to FIG. 2.
  • the steam generator according to FIG. 3 has the advantage that the control device for influencing the feed water supply can react very quickly to changes in the heat output which is transferred to the water evaporating in the tubes 4 of the tube wall 2. As a result, the effects of changes in the transferred heat output on the steam temperature in the reheating surfaces 12 and 13 remain extremely small.
  • the water separator 14 is a control device assigned, which is the same as in FIG. 2.
  • the steam generator according to FIG. 5 differs from the steam generator according to FIG. 2 essentially in that instead of the devices 22 and 23 for measuring the steam temperature and the steam pressure at the outlet end of the reheating surface 12, a steam flow meter 45 in the steam line 11 is attached, which is downstream of the post-heating surface 13 in terms of flow.
  • a transmitter 45a is assigned to this steam flow meter 45.
  • the output signal of the transducer 45a and the output signal of the transducer 27 assigned to the feed water flow meter 24 are fed to a device 46 with a computer for determining the ratio of the feed water flow in the feed water line 47 to the steam flow in the steam line 11, which leads from the feed water flow meter 24 and from the steam flow meter 45 be measured.
  • the device 46 for determining the ratio of the feed water flow in the feed water line 47 to the steam flow in the steam line 11 outputs an output signal to the controller 148, which is provided with a setpoint adjuster 147.
  • An injection steam cooler 50 is also connected downstream in the steam line 11 to the water separator 14, to which an injection water line 51 is connected.
  • a control valve 52 with motor drive 52a is located in this injection water line 51.
  • a controller 329 acts on this motor drive 52a, to which a setpoint adjuster 330 is assigned.
  • a device 322 e.g. thermocouple
  • a measuring transducer 325 is assigned to this device 322 and outputs an output signal to the controller 329.
  • the controller 329 increases the flow cross section of the control valve 52 when a predetermined steam temperature at the outlet end of the reheating surface 13 is exceeded and reduced this flow cross-section if this predetermined vapor temperature is not reached.
  • the output signal of the controller 148 and the output signal of the setpoint adjuster 35 are fed to a maximum value selection device 149, the output signal of which in turn is fed to the controller 37.
  • the output signal of the transducer 27 assigned to the feed water flow meter 24 is also connected to this controller 37, as in FIG.
  • the mode of operation of the controller 148, the setpoint adjuster 147, the maximum value selection device 149 and the setpoint adjuster 35 according to FIG. 5 corresponds to the mode of operation of the controller 29, the setpoint adjuster 30, the maximum value selection device 36 and the setpoint adjuster 35 of the steam generator according to FIG. 2.
  • the feed water flow through the feed water line 47 is always smaller by a predetermined proportion than the steam flow through the steam line 11.
  • a predetermined ratio of feed water flow through the feed water line 47 to the steam flow through the steam line 11, which is less than 1 a sufficiently large injection water flow can always occur through the injection water line 51 for injection into the injection steam cooler 50 in order to keep the steam temperature at the steam outlet of the reheating surface 13 at a constant value even in the event of faults.
  • FIG. 6 the same parts are also provided with the same reference symbols as in FIG. 2.
  • a control device is assigned to the water separator 14, which is designed in the same way as in FIG. 2.
  • the steam generator according to FIG. 6 differs from the steam generator according to FIG. 2 in particular in that the devices 22 and 23 for measuring the steam temperature and the steam pressure at the outlet end of the reheating surface 12 fall away.
  • an injection steam cooler 50 in the steam line 11 between the water separator 14 and the after-heating surface 13 is connected in terms of flow for injecting injection water, an injection water line 51 with a control valve 52 and associated motor drive 52a is connected instead, which starts from a feed water pump, not shown.
  • the injection water line 51 has an injection water flow meter 53 in terms of flow between the injection steam cooler 50 and the control valve 52.
  • the outlet end of the after-heating surface 13 is provided with a device 322 (eg thermocouple) which either measures the steam temperature at this outlet end or the material temperature corresponding to this steam temperature at this outlet end.
  • This device 322 is assigned a transducer 325 (signal transducer) which emits an output signal to a controller 329 which acts on the motor drive 52.
  • the controller 329 is provided with a setpoint adjuster 330.
  • the controller 329 increases the flow cross-section of the control valve 52 when a predetermined constant steam temperature at the outlet end of the after-heating surface 13 is exceeded, and reduces this passage cross-section when the predetermined constant steam temperature at the outlet end of the after-heating surface 13 falls below.
  • a measuring transducer 54 belongs to the injection water flow meter 53. From this measuring transducer 54 an output signal is led to a device 55 having a computer, to which the output signal of the measuring transducer 27 for the feed water flow meter 24 is also led. The device 55 determines the ratio of the injection water flow into the injection steam cooler 50 through the injection water line 51 to the feed water flow through the feed water line 47. The output signal from the device 55 is fed to a controller 57, which is provided with a setpoint adjuster 56.
  • the output signals of the controller 57 and a setpoint adjuster 35 are also routed to a maximum value selection device 58, the output signal of which is in turn routed to a controller 37.
  • the output signal of the transmitter 27 assigned to the feed water flow meter 24 is connected to this controller 37.
  • the mode of operation of the controller 57, the setpoint adjuster 56, the maximum value selector 58 and the setpoint adjuster 35 corresponds to the mode of operation of the controller 29, the setpoint adjuster 30, the maximum value selector 36 and the setpoint adjuster 35 of the steam generator according to FIG.
  • the steam generator according to FIG. 6 has the advantage that, for a given ratio of the injection water flow through the injection water line 51 to the feed water flow through the feed water line 47 of e.g. 0.05 a sufficiently large flow of injection water is always available through the injection water line 51 into the injection steam cooler 50.
  • the steam temperature at the steam outlet of the after-heating surface 13 can be kept at a constant value.
  • No steam flow meter is required in the steam line 11, so that this steam line 11 behind the reheating surface can also consist of several mutually parallel sub-lines.
  • the feed water line 47 can also open into the downpipes 8 with the economizer 48. Due to the relatively high density of the feed water introduced into the downpipes 8, the static water pressure in the downpipes 8 is relatively high. This also results in a relatively high pressure in the inlet header 6, so that the natural circulation through the downspouts 8 and the tubes 4 of the tube wall 2 is maintained even at a relatively high vapor pressure in the tubes 4.
  • the feed water line 47 at Steam generator according to FIG 7 at the mouth into the downpipes 8 - as shown in FIG 8 - is designed as a driving nozzle 81 of a jet pump 80. While the propellant nozzle 81 is connected to the propellant connection of the jet pump 80 via the feed water line 47 to the economizer 48, each drop pipe 8 forms the diffuser 83 of the jet pump 80 with a pressure port connected to the inlet manifold 6 and the head 85 of the jet pump 80 with a suction port 84 connected to the outlet manifold 7.
  • the water flow 86 flowing into the jet pump 80 from the economiser 48 draws a water flow 87 out of the outlet collector 7. Both water flows 86 and 87 are combined in the diffuser 83 to form a single water flow 88 which flows into the inlet header 6 at a relatively high pressure.
  • the jet pump 80 is expediently arranged in the local vicinity of the inlet header 6 or part of the water flow emerging from the economicer 48 into the downpipe 8 in front of the suction port 84 initiated.
  • Each of the two measures causes the water flow 87 to be subcooled and thus prevents the formation of steam in the jet pump 80.
  • each down pipe 8 in FIG. 7 is larger than the inside cross section of each of the pipes 4 of the pipe wall 2, so that the frictional pressure loss in the down pipes 8 is significantly lower than in the pipes 4 of the pipe wall 2. This also increases the natural circulation the downpipes 8 and the tubes 4 of the tube wall 2 achieved.
  • each tube 4 of the tube wall 2 opening into the outlet header 7 has a fitting 96 located in the tube wall 2, via which the tube 4 in question is fastened to an additional tube 90 of the tube wall 2.
  • This Additional pipe 90 is connected to the outlet header 7 via a connecting pipe 91.
  • the additional pipes 90 are part of the pipe wall 2 and connected to an end header 92 at their upper end. From the end collector 92, which is located on the outside of the vertical throttle cable of the steam generator at a locally higher level than the outlet collector 7, the steam line 11 with the reheating surfaces 12 and 13 finally comes off.
  • the additional pipes 90 of the pipe wall 2 form an additional heating surface. Due to this additional heating surface, the natural circulation system determined by the pipes 4 and the down pipes 8 is located near the burners for fossil fuel in the openings 99 of the pipe wall 2 according to FIG. 1 the water in these tubes 4 has a much lower density than the water in the unheated downpipes 8 on the outside of the throttle cable of the steam generator. This favors natural circulation in the pipes 4 of the pipe wall 2 and in the down pipes 8 even when the steam generator is at very high pressure, e.g. supercritical pressure is operated.
  • the feed water line 47 containing the economizer 48 is connected to this series header 93.
  • This series header 93 has a locally lower level than the inlet header 6.
  • Additional tubes 94 originate from the front header 93, which belong to the tube wall 2 and form an additional heating surface in this tube wall 2. Each upper end of these additional pipes 94 merges into a pipe 4 of the pipe wall 2, which is connected to the inlet header 6.
  • Both the downpipes 8 leading to the inlet header 6 and the tubes 4 of the gas-tight tube wall 2 are connected to the outlet header 7 of the steam generator according to FIG. Further is the steam line 11 with the reheating surface 12 is also connected directly to the outlet header 7.
  • the additional heating surface formed by the additional tubes 94 also causes the entire length of the tubes 4 of the tube wall 2 to be heated particularly strongly by the burners for fossil fuel in the openings 99 of the tube wall 2.
  • the water in the tubes 4 of the tube wall 2 has a very much lower density than the water in the unheated downpipes 8 on the outside of the gas train of the steam generator, so that natural circulation in the tubes 4 of the tube wall 2 and the downpipes 8 is then even more favorable is when the steam generator with very high pressure, e.g. supercritical pressure is operated.
  • a steam generator can also form in the gas-tight tube wall 2 both an additional heating surface with additional tubes 90 leading to an end header 92 as shown in FIG. 7 and an additional heating surface with additional tubes 94 leading to an upstream header 93 as shown in FIG.
  • the tubes 4 of the tube wall 2 insofar as they have their ends 4a and 4b, on the inlet header 6 and on the outlet header 7 are connected, have a larger internal cross section than the additional tubes 94 starting from the upstream header 93 and as the additional tubes 90 and connecting tubes 91 which lead from the outlet header 7 to the end header 92. This results in a particularly low loss of frictional pressure in the tubes 4 and promotes natural circulation in these tubes 4 and the downpipes 8.
  • this pipe 4 of the pipe wall 2 can have inner ribs 104 arranged in a screw shape. These inner fins 104 cause the water content of that in the tubes 4 Water-steam mixture (wet steam) preferably flows on the inside of the wall of the tubes 4 and the steam portion in the center of these tubes 4, so that these tubes 4 are still well cooled even at low mass flow density, for example at part-load operation, and subcritical pressure.
  • Water-steam mixture wet steam
  • this fitting 96 can also advantageously be in the intermediate wall 105, such as Shown in longitudinal section in FIG. 12, form a passage opening 97 from the pipe 4 to the additional pipe 90, the passage cross section of which is smaller than the inner cross section of the pipe 4.
  • This passage opening 97 reduces the flow through the outlet header 7 and thus also the pressure loss in this outlet header 7 and thus favors the natural circulation in the pipes 4 and the downpipes 8.
  • a collar 98 formed on the side of the tube 4 of the tube wall 2 at the passage opening 97 in the intermediate wall 105 and surrounding the passage opening 97 can prevent water components of the wet steam in the tubes 4 from reaching the additional tube 90 through the passage opening 57.
  • the tubes 4 of the tube wall 2 open tangentially into the hollow cylindrical wall of the outlet header 7 and the additional tubes 90 of the tube wall 2 extend radially from this wall.
  • the water-steam mixture entering the outlet manifold 7 through the pipes 4 thus has a swirl which, particularly when the steam generator is operated at partial load at subcritical pressure, leads to a water-steam separation in the outlet manifold 7.
  • the radial exit of the additional tube 90 preferably at the top of the outlet header, largely prevents the additional tubes 90 in the outlet header 7 from being in these additional tubes 90 separated water is entrained.
  • the downpipes 8 also extend radially from the hollow cylindrical wall of the outlet header 7.
  • FIG. 14 too, the same parts are provided with the same reference symbols as in FIG. 2.
  • a control device is assigned to the water separator 14, which is of the same design as in FIG. 2.
  • the steam generator according to FIG. 14 differs from the steam generator according to FIG. 2 essentially in that instead of the devices 22 and 23 for measuring the steam temperature, the steam pressure at the outlet end of the After-heating surface 12 in the steam line 11 according to FIG. 14 between the outlet header 7 and the after-heating surface 12 there is a venturi tube 209 with - as the longitudinal section according to FIG. 15 shows - a venturi constriction 210 of the inner tube cross section.
  • venturi tube 209 From the venturi tube 209, two electrodes 211a and 211b of an electrical capacitor are attached to the venturi constriction 210, which are provided with a coating of electrically insulating material and between which the interior of the venturi tube 209 is located at the venturi constriction 210.
  • a transducer 211c is connected to the electrodes 211a and 211b and outputs an output signal corresponding to the capacitor capacitance.
  • thermocouple for measuring the steam temperature in the pipe of the steam line 11 directly in front of the venturi 210, to which a transmitter 212c is assigned.
  • a pressure measuring tube 213 from the smallest inner tube cross section of the venturi constriction 210 and a pressure measuring tube 214 seen in the flow direction of the steam line 11 also run off at the side with the largest inner tube cross section in front of the venturi constriction 210.
  • Pressure measuring tube 213 and pressure measuring tube 214 lead to a differential pressure meter 215 (eg spring differential pressure meter), to which a transmitter 213c is connected, which emits an output signal which corresponds to the difference between the vapor pressures at the point of the largest pipe inner cross section and at the point of the smallest pipe inner cross section.
  • a differential pressure meter 215 eg spring differential pressure meter
  • the pressure measuring tube 214 also leads to a pressure meter 216 (for example a spring pressure meter), to which a measuring transducer 214c is connected, which emits an output signal which corresponds to the vapor pressure at the location of the largest tube internal cross section (cf. US Pat. No. 4,829,831).
  • a pressure meter 216 for example a spring pressure meter
  • the transducers 211c, 212c, 213c and 214c each output their output signal to a device 240 for determining the residual moisture of the steam flowing in the steam line 11.
  • This device 240 outputs its output signal, which corresponds to the residual moisture of the steam in the steam line 11 according to FIG. 14, to a controller 241, which is provided with a setpoint adjuster 242.
  • the output signal of the controller 241 and the output signal of a setpoint adjuster 35 are fed to a maximum value selection device 243, the output signal of which is applied to a controller 37.
  • the output signal of the transmitter 27, which is assigned to the feed water flow meter 24, is also present at the controller 37.
  • the mode of operation of the controller 241, the setpoint adjuster 242, the maximum value selector 243 and the setpoint adjuster 35 corresponds to the mode of operation of the controller 29, the setpoint adjuster 30, the maximum value selector 36 and the setpoint adjuster 35 of the steam generator according to FIG. 2.
  • a steam generator according to FIG 14 has the advantage that the control device for influencing the feed water supply can react very quickly to changes in the heat output which is transferred to the water evaporating in the tubes 4 of the tube wall 2 and the tube sheet 3, since the measured variables for Determining the residual moisture of the steam in the steam line 11 is recorded immediately behind the gas flue with the pipe wall 2, on which the burners for fossil fuel are located in the openings 99.
  • the residual moisture of the steam in the steam line 11 is only suitable as a controlled variable as long as the pressure in the steam generator according to FIG. 14 is below the critical pressure. If the critical pressure is reached, the device 240 for determining the residual moisture of the steam, which gives an output signal corresponding to the residual moisture of the steam in the steam line 11, must be switched off and one of the control devices as shown in FIGS. 2, 3, 5 or 6 switched on.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Control Of Steam Boilers And Waste-Gas Boilers (AREA)
  • Chimneys And Flues (AREA)
  • Air Humidification (AREA)
  • Organic Low-Molecular-Weight Compounds And Preparation Thereof (AREA)
EP90124271A 1990-01-31 1990-12-14 Dampferzeuger Expired - Lifetime EP0439765B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP90101940 1990-01-31
EP90101940 1990-01-31

Publications (2)

Publication Number Publication Date
EP0439765A1 EP0439765A1 (de) 1991-08-07
EP0439765B1 true EP0439765B1 (de) 1995-05-03

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ID=8203573

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EP90124271A Expired - Lifetime EP0439765B1 (de) 1990-01-31 1990-12-14 Dampferzeuger

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US (1) US5056468A (ja)
EP (1) EP0439765B1 (ja)
JP (1) JP3174079B2 (ja)
AT (1) ATE122137T1 (ja)
CA (1) CA2035198A1 (ja)
DE (1) DE59009015D1 (ja)
DK (1) DK0439765T3 (ja)

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JP2563099B2 (ja) * 1992-05-04 1996-12-11 シーメンス アクチエンゲゼルシヤフト 強制貫流蒸気発生器
US5209188A (en) * 1992-06-01 1993-05-11 The Babcock & Wilcox Company Fluid bed combustion reheat steam temperature control
DE19504308C1 (de) * 1995-02-09 1996-08-08 Siemens Ag Verfahren und Vorrichtung zum Anfahren eines Durchlaufdampferzeugers
US5713311A (en) * 1996-02-15 1998-02-03 Foster Wheeler Energy International, Inc. Hybrid steam generating system and method
DE19623457A1 (de) * 1996-06-12 1997-12-18 Siemens Ag Verfahren zum Betreiben eines Solarkraftwerkes mit wenigstens einem solaren Dampferzeuger und Solarkraftwerk
EP1288567A1 (de) * 2001-08-31 2003-03-05 Siemens Aktiengesellschaft Verfahren zum Anfahren eines Dampferzeugers mit einem in einer annähernd horizontalen Heizgasrichtung durchströmbaren Heizgaskanal und Dampferzeuger
EP1533565A1 (de) * 2003-11-19 2005-05-25 Siemens Aktiengesellschaft Durchlaufdampferzeuger
US7882809B2 (en) * 2006-11-07 2011-02-08 L'air Liquide, Societe Anonyme Pour L'etude Et L'exploitation Des Procedes Georges Claude Heat exchanger having a counterflow evaporator
EP2065641A3 (de) * 2007-11-28 2010-06-09 Siemens Aktiengesellschaft Verfahren zum Betrieben eines Durchlaufdampferzeugers sowie Zwangdurchlaufdampferzeuger
CN101910776B (zh) * 2008-01-14 2013-12-04 巴布科克和威尔科克斯能量产生集团公司 换热器
JO3344B1 (ar) * 2008-10-24 2019-03-13 Babcock & Wilcox Co مبادل حراري لمستقبل شمسي مجمع في المشغل
DE102013202249A1 (de) * 2013-02-12 2014-08-14 Siemens Aktiengesellschaft Dampftemperatur-Regeleinrichtung für eine Gas- und Dampfturbinenanlage
DE102013003386B4 (de) * 2013-03-01 2020-08-13 Nippon Steel & Sumikin Engineering Co., Ltd. Verfahren und Vorrichtung zum Betreiben eines Dampferzeugers in einer Verbrennungsanlage
CN103422919B (zh) * 2013-07-19 2015-03-11 高椿明 一种喷水注入式脉冲蒸汽发电系统及方法
CN111780084B (zh) * 2020-07-31 2022-03-04 中国能源建设集团广东省电力设计研究院有限公司 一种锅炉超前加速优化的控制方法、装置及存储介质
CN112098131B (zh) * 2020-09-15 2021-12-24 上海交通大学 模拟核主泵进口非均匀来流的蒸汽发生器模拟装置
CN114738724A (zh) * 2022-04-29 2022-07-12 泰州市斯迪蒙科技有限公司 一种新型蒸汽发生装置

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US3297004A (en) * 1965-08-26 1967-01-10 Riley Stoker Corp Supercritical pressure recirculating boiler
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EP0308728B1 (de) * 1987-09-21 1991-06-05 Siemens Aktiengesellschaft Verfahren zum Betreiben eines Durchlaufdampferzeugers

Also Published As

Publication number Publication date
CA2035198A1 (en) 1991-08-01
JPH04214101A (ja) 1992-08-05
US5056468A (en) 1991-10-15
JP3174079B2 (ja) 2001-06-11
EP0439765A1 (de) 1991-08-07
ATE122137T1 (de) 1995-05-15
DK0439765T3 (da) 1995-10-02
DE59009015D1 (de) 1995-06-08

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