US3096743A - Steam generator - Google Patents

Steam generator Download PDF

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US3096743A
US3096743A US819102A US81910259A US3096743A US 3096743 A US3096743 A US 3096743A US 819102 A US819102 A US 819102A US 81910259 A US81910259 A US 81910259A US 3096743 A US3096743 A US 3096743A
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steam
control
temperature
reheaters
coupled
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US819102A
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Profos Paul
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Sulzer AG
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Sulzer AG
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22G—SUPERHEATING OF STEAM
    • F22G5/00—Controlling superheat temperature
    • F22G5/20—Controlling superheat temperature by combined controlling procedures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
    • F01K7/16—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being only of turbine type
    • F01K7/22—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being only of turbine type the turbines having inter-stage steam heating
    • F01K7/24—Control or safety means specially adapted therefor
    • 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
    • F22B29/10—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 with sliding point of final state of complete evaporation
    • 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
    • F22B35/10—Control systems for steam boilers for steam boilers of forced-flow type of once-through type
    • F22B35/108—Control systems for steam generators having multiple flow paths
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22G—SUPERHEATING OF STEAM
    • F22G5/00—Controlling superheat temperature
    • F22G5/02—Applications of combustion-control devices, e.g. tangential-firing burners, tilting burners
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22G—SUPERHEATING OF STEAM
    • F22G5/00—Controlling superheat temperature
    • F22G5/06—Controlling superheat temperature by recirculating flue gases

Definitions

  • This invention relates to a steam generator including a least two tube systems each traversed by a part of the working substance and each including a reheater for partialiy expanded steam.
  • a steam generator including a least two tube systems each traversed by a part of the working substance and each including a reheater for partialiy expanded steam.
  • water or steam is to be understood as including any other working substance suitable for use in a boiler.
  • a bypass line around the heat exchanger with a suitable flow control means therein, the bypass line being either in the channel of the steam to be reheated or in that of the high pressure steam which is employed to heat or to cool the steam to be reheated.
  • the temperature to which the partly expanded steam is reheated hereinafter called the reheat tempera ture, can also be controlled with the help of stack gases, either by means of partial and controlled bypassing of the steam to be reheated around reheater surfaces heated by such gases or by control of the application of such gases themselves to the reheater.
  • the invention surmounts this difficulty, without substantial increase in the requirements of the system for control apparatus.
  • a steam generator according to the invention there are provided, for control of the superheated temperature to which the steam is reheated, means which are capable of altering in the same sense or direction the heat transfer in all such tube systems, i.e. of raising the heat transfer in all, or lowering it in all.
  • Coupled control means in contra-distinction to individual or differential control means operating on one or more tube systems to the exclusion of others, or raising the heat transfer in one while lowering it in another.
  • the invention further provides, in order to extend the range of reheat temperature control, supplementary coupled control means operating on each of a plurality of tube systems.
  • control means are subjected to the effect of control impulses dependent on the temperature of reheat achieved in at least one of the tube channels.
  • a further control signal representative of that temperature is in that channel superposed on the control signal which is applied to the additional means above referred to.
  • the invention is based on a recognition of the fact that the range of load values over which the reheat temperatures may be controlled can be substantially increased by the provision of additional or supplementary means to change in the same sense the heat transfer rate in all of the tube systems and on the further fact that provision of separate means for individual control of the reheat temperatures in a single one of the tube systems requires only a minor increase in the total amount of control apparatus.
  • a means provided for coupled control of heat transfer in the plural tube systems of the boiler may take the form of coupled Water injectors for the addition of water to the high pressure steam before its introduction into 'the heat exchangers.
  • the coupled control means may take the form of rate of flow control devices disposed in bypass connections for the high pressure steam around the heat exchangers.
  • one of the coupled control means may take the form of rate of flow control devices coupled together, and disposed in bypass lines for the steam to be reheated, these lines being connected around at least a portion of the reheater heat transfer surfaces.
  • one of the coupled control means may take the form of means for control of the flow of stack gases which divert a part of the stack gases around at least part of the reheater surfaces.
  • a coupled means for control of reheat temperature in plural tube systems may take the form of means to control the quantity of stack gases so recirculated.
  • both the first and supplementary coupled control means can be made to depend upon control signals derived from an average of the reheat temperatures at all reheaters.
  • a single control impulse may be employed, derived from the reheat temperature of the reheater in a single one of the tube systems.
  • the supplementary coupled control means may then take the form of water injectors operating on the high pressure steam before its application to the reheater heat exchangers, the position of the movable burners and the volumes of injected water being subjected to control by a signal derived from the sum of the two reheat temperatures.
  • the signal employed for control of the quantity of injected water may be made dependent on the difference of the two reheat temperatures.
  • FIG. 1 is a schematic diagram of a steam generator according to the invention including two tube systems, movable burners disposed in a common firing space, and water injector means operating on the steam at high pressure before its entry into heat exchangers traversed by partly expanded steam;
  • FIG. 2 is a diagram similar to that of FIG. 1 but showing a modification of the invention relating particularly to the control apparatus;
  • FIG. 3 is a diagram of a steam generator according to the invention having two tube systems and movable burners in a common firing space, and bypass means for the steam to be reheated about a part of the reheater heating surfaces;
  • FIG. 4 is a schematic diagram of another steam generator according to the invention having two tube systems and movable burners in a common firing space, and having means for bypassing part of the high pressure steam about the heat exchangers in which the partly expanded steam is to be reheated by that high pressure steam; and
  • FIG. 5 is a diagram similar to that of FIG. 1 but showing a further modification of the invention including recirculation of the products of combustion in the boiler and injection of water into the high pressure steam before its introduction into the heat exchangers.
  • steam or other vaporized working substance emerging from feed water preheating and vaporizing devices not shown enters one of two parallel-connected tube systems at 11 and passes through an initial superheater 12.
  • this tube system it then passes through a line 13 into a heat exchanger 14, preferably disposed within the radiation zone of the boiler fire.
  • the steam emerging at high pressure from line 13 passes through the inner tube 15 of the exchanger 14 whereas partly expanded steam is passed through the outer tube 16 which surrounds the inner tube 15.
  • the high pressure steam finally passes through a third superheater surface 17 and through the line 18 into the high pressure end of a turbine, not shown.
  • Partly expanded steam extracted from the turbine enters the exchanger l14 at a line 19, passing through the outer tube 16 thereof.
  • this partly expanded steam will be either heated or cooled, according to the relation of its temperature to that of the high pressure steam in the inner tube 15. If desired, superheater elements, heated by the products of combustion, may be inserted into the flow path of the partly expanded steam.
  • the partly expanded steam after passage through the exchanger 14 passes through a line 20 into the portion 21 of the r-eheater, for re-superheating of the partly expanded steam.
  • the steam so reheated passes through the line 22 into the low pressure portion of the turbine and is thence delivered to a condenser (not shown) in known fashion.
  • the elements 11 to 22 constitute part of a first tube system.
  • a second tube system includes corresponding elements identified at corresponding reference characters 11' to 22.
  • a water injector line 23' which includes a rate of flow control device 24' therein.
  • Line 23' opens into the final superheater 17'.
  • the control device 24' is made responsive to temperature measurements at the inlet and outlet ends of the superheater 17', such measurements being made by temperature measuring devices 26 and 25'.
  • a similar temperature regulating system including elements 23, 24, 26 and 25 is associated with the superheater 17 of the first tube system.
  • the steam generator is fired by means of movable burners 31 and 31' which are disposed in a single firing space including both of the tube systems which have been described.
  • the two burners are mechanically linked together by means of linkages diagrammatically indicated at 32, 33 and 34.
  • a tubular element 35 is affixed to the support bar 33, and the element 35 is supported at bearings 36 for translatory motion as indicated by the arrows 37. Motion of the bar 33 downward in the figure, in the direction identified by the minus sign associated with arrows 37, shifts the burners in the direction identified by the minus signs associated with arrows 38, and vice versa.
  • the movable burners constitute a first coupled means for adjustable control of the heat absorption in the two tube systems, i.e. changes produced by this means being in the same sense at both tube systems.
  • the setting of these means is governed by a control signal which is a function of the reheat temperatures in the two tube sys tems.
  • temperature measuring elements are provided at 41 and 42 in the lines 22 and 22'. These temperature measuring devices generate temperaturerespresentative signals in form of pressures in the hydraulic lines 43 and 44 by conventional apparatus, the details of which are not shown.
  • the pressure in line 52 operates on the body 53 of a valve 53' forming part of a servo motor which includes a fixed cylinder 54 and a piston 55 therein, controlling the position of a rod 56.
  • a plate 57 is pinned to the rod 56 and a spring 58 is engaged between the plate 57 and the bar 33.
  • the rod 46 moves in the downward or negative direction indicated by the negative sign associated with arrows 59.
  • the pressure signal thus generated in line 52 pushes the valve body 53 downward, permitting hydraulic fluid to flow into the valve 53 under pressure at a line 60 from a reservoir not shown.
  • This fluid passes through valve 53 to the upper side of piston 55, lowering the latter, causing a lowering of the bar 33 in the negative sense of arrows 37 and a shift of the movable burners in the negative sense of their arrows 38.
  • Heat transfer in the two tube systems is thereby changed, in the same sense for both, diminishing the heat applied to the reheaters which comprise exchangers 14 and 14 and superheaters 21 and 21'.
  • the sum of the two temperatures and t accordingly constitutes a control signal for the system shown, dependent on the average value of the two reheat temperatures.
  • Shift in the position of the burners is limited by stops 61 on the motion of bar 33.
  • the generator of FIG. 1 includes supplementary coupled control means on the heat transfer to the two tube systems. These take the form of water injectors, for injecting water from the line 71 into the lines 13 and 13.
  • rate of flow control devices 72 and 72' are provided whose rates of flow are adjusted together in the same sense by motion of the rod 73.
  • This rod controls the two valves 72 and 72' by means of a lever 74, to whose midpoint it is pivotally coupled.
  • Rod 73 is coupled to rod 56 via a link generally indicated at 75 comprising a cage or cylinder 75 attached to rod 56 and a piston 75" fitting loosely in the cage, the piston being attached to rod 73.
  • Link 75 thus provides a specified amount of play between rods 56 and 73, parallel to their own length.
  • rod 73 will be held by spring 76 in the position defined by abutment of plate 77' (pinned to red 73) on stop 77. Spring 76 is engaged between the plate 77' and an abutment 77".
  • the supplementary coupled control means on the heat transfer in the two tube systems constituted by the water injector apparatus shown will come into operation only when the first coupled control means comprising the movable burners have reached the limit of their travel. In this way the quantities of injected water are under normal circumstances held to low values, which is thermodynamically advantageous.
  • a supplementary control signal which is a function of the temperature of the reheated steam.
  • the apparatus enclosed within the dash line box 81 develops a signal corresponding to the difierence between the two reheated steam temperatures t; and
  • the pressure in the line 44 is applied to a piston 82 in a fixed cylinder 83 and the pressure in line 43 is applied to a similar piston 84 in a fixed cylinder 85.
  • the motions of the pistons which occur upon changes in temperatures 1 and t, are subtracted from each other by means of the lever 86 to which the pistons are coupled, and the resultant motion of the rod 87 coupled to piston 84 controls the position of a control piston 88.
  • the first coupled means for control of the reheater temperatures comprise again movable burners 31 and 31' disposed with the tube systems in a common firing space.
  • the position of these burners, which move together in the same sense with respect to increase or decrease of heat applied thereby to their tube systems, is in this embodiment controlled exclusively by the temperature measured at a device 101 in line 22.
  • the temperature measuring device 101 consequently generates a pressure signal, in a known manner, in the hydraulic line 102.
  • This signal, representative of the temperature is communicared through a bellows 103, into motion of a rod 104 and thence to lever 105 which adjusts a servo control valve 106.
  • the elements are so proportioned that increase in the temperature t above a reference level, which can be adjustably set by means not shown, shifts the burners in the direction indicated by the minus sign associated with arrows 110. This reduces the application of heat to the reheating coils 21 and 21'. In consequence, temperatures is returned to its reference value.
  • supplementary means are provided, as in the embodiment of FIG. 1, for control of the heat transfer to the two tube systems.
  • These supplementary means may take the form of a water injector system for adjustment in the same sense of the rate at which water is injected from the conduit 111 into the high pressure steam lines 13 and 13.
  • valves 112 and 112' are cont-rolled by a linkage comprising a rod pinned to bar 108 and levers 113 and 114 coupled to bar 115. The opening of both valves is thus changed in the same direction simultaneously with change in the position of the burners, it being assumed for the moment that the right hand end of lever 114 constitutes a fixed fulcrum.
  • a value for the temperature r above the correct or reference value therefor thus produces not only a shift in the position of the burners for reduced heat application as already described but also an opening of both valves 112 and 112.
  • the provision of valves 112 and 112' thus connected to the mechanism for change in the burner position thus extends the control range on the temperatures and whereby desired reheat temperatures can be maintained over a wider range of loads on the system, corresponding to a wider range of steam flow rates.
  • the first means for coupled control (i.e. in the same sense) of the rate of heat transfer to the two tube system again comprise movable burners 134 and 134'. Their position is controlled. by the level of the temperature t which is made effective through a hydraulic line 135 on servo control pistons 136 and 136 linked to the burners. The operation may be that described in conjunction with FIG. 2.
  • supplemenary means comprise rate of flow control valves 137 and 137' disposed in bypass lines 138 and 138' which are connected in parallel with the intermediate reheater superheater surfaces 133 and 133'. According as more or less of the working substances flows through the lines 138 and 138, the temperatures t and 2 are lowered or raised.
  • the two valves 137 and 137' are subjected to the same control signal, as are the positions of burners 134 and 134'.
  • the line 135 is connected through an extension line 139 to servo control pistons 137a and 137b which are coupled to the valves 137 and 137' respectively.
  • a temperature above the correct value effects an opening in both of the valves 137 and 137'.
  • control signal which is a function of the temperature t and which serves for adjustment of that valve alone, with consequent efiect upon the temperature t A temperature t above the reference value effects opening of the valve 137 and vice versa, by operation on the servo control piston 137a through a hydraulic control signal line 140.
  • the first coupled means for adjusting, in the same sense, the rate of heat transfer in the two tube systems comprise again movable burners 141 and 141'.
  • the position of these burners may be controlled by mechanism similar to that in FIG. 3 including a temperature-representative signal generating device 1 connected through a signal channel 2 with servo control pistons 3 and 3' coupled to burners 141 and 141'.
  • a temperature-representative signal generating device 1 connected through a signal channel 2 with servo control pistons 3 and 3' coupled to burners 141 and 141'.
  • the supplementary means for coupled control of the rate of heat transfer to the two tube systems comprises rate of flow control valves 142 and 142, disposed in bypass lines 143 and 143' which are connected around the inner coils 15 and 15 of heat exchangers 14 and 14' respectively.
  • rate of flow control valves 142 and 142 disposed in bypass lines 143 and 143' which are connected around the inner coils 15 and 15 of heat exchangers 14 and 14' respectively.
  • the reheat temperatures t and are lowered or raised.
  • Adjustment of the two valves 142 and 142' together in the same sense extends the control range of the reheat temperatures as does coupled adjustment of the valves 137 and 137' in the embodiment of FIG. 3.
  • the valves 142 and 142' are controlled for motion together in the same sense by servo control pistons 4 and 4, which are connected to the signal channel 2.
  • servo control pistons 4 and 4 which are connected to the signal channel 2.
  • the working substance enters, from a feed water p-reheater not shown, into the vaporizing coil 151 of one tube system and passes therefrom into an initial superheater 152. It then passes through a conduit 154 into the coil 156 of a heat exchanger 155, disposed outside the wall of the firing space, shown fragmentarily at 149. In the exchanger 155 the newly vaporized steam entering through line 154 serves either to heat or to cool the partially expanded steam fed from the turbine to the heat exchanger at line 157.
  • the high pressure steam then passes from coil 156 through a second superheater 158 and through a conduit 159 to the high pressure end of the turbine, not shown.
  • Partially expanded steam extracted from the turbine passes, as already stated, through the line 157 into that portion of heat exchanger 155 outside the coil 156 and from thence to the reheater surface 160, indicated diagrammatically as a coil.
  • the steam so reheated passes through the line 161 into the low pressure end of the turbine and is withdrawn therefrom to a condenser.
  • FIG. 5 the elements identified with reference characters 151 to 161 form part of the first tube system.
  • a second corresponding tube system includes elements identified at reference characters 151 to 161'. Both tube systems are heated in a common firing space by means of a burner 162.
  • a flue gas return arrangement comprising a conduit 162' in which there is provided a blower 163. A portion of the stack gases is returned by these means from the upper end of the boiler to a point closer to the fire.
  • the quantity of the products of combustion so recirculated can be adjusted by means of a damper valve 164, coupled to a rod 165.
  • Rod 165 is in turn coupled to a lever 166 to whose midpoint is pivotally attached a bar 167. So long as the lever 166 stands clear of the stop 168, springs 169 and 170 maintain the lever 166 in a specified angular position, e.g. perpendicular, to the bar 167.
  • the bar 167 may be controlled in position by a servo motor 54 as illustrated in FIG. 1 with respect to the bar 33 of that figure. Adjustment in the position of bar 167 is thus so made that when the sum of reheat temperatures r and t in lines 161 and 161 of FIG. 5 lies above the sum of their reference values, the quantity of recirculated flue gases is reduced by lowering of bar 167, which produces a partial closing of damper 164, and vice versa-so long as bar 166 clears stop 168.
  • the supplementary coupled means for controlling in the same sense the rate of heat transfer in the two tube systems are again, as in the embodiment of FIG. 1, provided in the form of Water injectors by means of which water provided at a conduit 172 can be injected into the high pressure steam lines 154 and 154 through additional conduits 173 and 173' respectively.
  • the openings of valves 174 and 174 in these last-named lines are changed together in the same sense by motion of the bar 175, which is coupled through a limited lost motion linkage 176 like the linkage 75 of FIG. 1 with the left end of the lever 166.
  • this arrangement results in adjustment of the supplementary control means at valves 174 and 174' only when the control range of the first means comprising valve 164 has been exhausted by engagement of bar 164 against stop 168.
  • the lever 177 may be rotated about its point of connection to lever by means similar to those described in connection With FIG. 1 as operative on the lever 74 of that figure.
  • the invention provides, in steam generators having plural heaters and tube systems, improved means for control of reheat temperature by control of the heat source or sources which operate on the reheaters, either directly or via freshly vaporized steam brought into heat exchange relation
  • control of the temperature of that fresh steam through water injection or like means
  • bypass means of the relative quantities of fresh and reheat steam so brought into heat exchange relationship
  • control of recirculation of stack gases flowing over fresh steam or reheat steam coils or both by the provision of bypass means about such reheat steam coils, and by combinations of these arrangements, and by application of these control means individually or difierentially to the separate reheaters, as cumulatively thereto.
  • heating exchange surfaces schematically shown in the drawings may comprise plural tubes or groups of tubes.
  • various control means are provided in the high pressure steam tube systems, operating with respect to rate of steam flow, pressure and temperature.
  • the invention is applicable to both forced circulation and natural circulation boilers, but is employed with particular advantage in steam generating plants operating at supercritical conditions.
  • a steam generator comprising firing means, at least two parallel-connected tube systems each including a heheater, said generator further comprising first and second means for varying in the same sense the amount of heat transferred to partially expanded steam in each of said reheaters, means responsive to the temperature of the steam reheated in at least one of said reheaters for operating said first and second means to increase said amounts upon decline of said temperature and vice versa, and supplementary means responsive to the temperature of the steam reheated in one of said reheaters for additionally varying the amount of heat transferred to partially expanded steam passing through said one reheater.
  • a steam generator comprising firing means, at least two parallel-connected tube systems each including a reheater, said generator further comprising first and second means for varying in the same sense the amount of heat transferred partially expanded steam in each of said reheaters, means responsive to change in the sum of the temperatures of the steam reheated in said two reheaters for operating said first and second means to increase said amounts upon decline of said sum and vice versa, and supplementary means responsive to change in the difference between the temperatures of the steam reheated in said two reheaters for additionally varying in opposite snses the amounts of heat transferred at said two reheaters to partially expanded steam passing therethrough, said last-named means varying, as to that one of said tube systems in whose preheater the change of temperature predominates in a change of said difference, the heat transferred to such tube system inversely with the sign of the change in reheated steam temperature in such tube system.
  • a steam generator comprising firing means, a plurality of parallel-connected steam tube systems, a reheater associated with each of said tube systems, first and second reversibly movable means to change in the same sense the amount of heat transferred to partially expanded steam in each of said reheaters, a lost motion linkage means coupling said first and second means together, and means responsive to variation in the temperature of steam reheated in at least one of said reheaters to move one of said first and second means in the sense required to vary the rate of heat transfer in each of said reheaters as an inverse function of said steam temperature.
  • a steam generator comprising two tube systems connected in parallel for the flow of a Working substance between a condenser and a turbine, two reheaters connected in parallel for the flow of a working substance between a higher and a lower pressure stage of the turbine, a separate source of heat associated with each of said tube systems, separate first means to vary the amount of heat absorbed from said sources by partially expanded steam in each of said reheaters, separate second means to vary the amount of heat absorbed from said sources by partially expanded steam in each of said reheaters, first and second movable coupling means respectively coupling said separate first varying means together and coupling said separate second varying means together such that motion of either of said coupling means shifts both of the varying means coupled thereto in the same sense, a linkage including a lost motion for coupling said first and second movable coupling means to each other, motor means responsive to variations in the temperature of the partially expanded steam reheated in at least one of said reheaters, said motor means being coupled to one of said first and second movable coupling means to move
  • a steam generator comprising firing means, a plurality of tube systems connected in parallel between a condenser and a high pressure stage of a turbine, a reheater associated with each of said tube systems, said reheaters being connected between two different pressure stages of said turbine, each of said reheaters comprising means to exchange heat between fresh steam in one of said systems and partially expanded steam and a reheater coil adapted to absorb heat from said firing means, said generator further comprising first reversibly movable means to change in the same sense the rate of heat exchange between said firing means and each of said tube systems, second reversibly movable means to change in the same sense the rate of heat exchange between fresh steam and partially expanded steam in each of said reheaters, a lostmotion linkage means coupling said first and second reversibly movable means together, and supplementary means responsive to variation in the temperature of steam reheated in at least one of said reheaters to additionally move one of said first and second reversibly movable means in the sense required to vary the rate of heat exchange controlled by
  • a steam generator comprising a plurality of steam tube systems each including a reheater, each of said reheaters including means to exchange heat with its associated tube system, said generator further including separate movable firing means for each of said systems, a separate flow regulating means for admission of water to each of said systems in advance of its heat exchange means, first movable means coupling said firing means together for reversible motion in the same sense with respect to their tube systems, second movable means coupling said flow regulating means together for reversible adjustment in the same sense, means linking said movable coupling means together, first motor means responsive to variations in the steam temperature in at least one of said reheaters to shift said linking means in the sense required to vary the exposure of said tube systems to said firing means as an inverse function and the opening of said flow regulating means as a direct function of said steam temperature and second motor means responsive to variations in the steam temperature in one of said reheaters to shift one of the firing and flow regulating means of the tube system including said one reheater in the sense required to vary the exposure of said last
  • each of said reheaters includes a bypass line and wherein one of said first and second means comprises a flow control means in each of said by-pass lines.
  • each of said reheaters includes a fresh steam line and a line for partially expanded steam, said lines being in heat exchange relation, and wherein said by-pass lines each by-pass one of the fresh steam and partially expanded steam lines of a separate one of said reheaters.
  • each of said reheaters comprises a fresh steam line and a partially expanded steam line in heat exchange relation
  • one of said first and second means comprises adjustable means to recirculate over said tube systems

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Regulation And Control Of Combustion (AREA)
  • Control Of Steam Boilers And Waste-Gas Boilers (AREA)
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US (1) US3096743A (fr)
BE (1) BE579611A (fr)
CH (1) CH360078A (fr)
FR (1) FR1224444A (fr)
GB (1) GB919262A (fr)
NL (2) NL229328A (fr)

Cited By (2)

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Publication number Priority date Publication date Assignee Title
US3202135A (en) * 1961-07-27 1965-08-24 Combustion Eng Vapor temperature control method
US3202138A (en) * 1961-07-27 1965-08-24 Combustion Eng Vapor temperature control method

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3151601A (en) * 1961-05-18 1964-10-06 Combustion Eng Apparatus for combustion control of multiple furnace steam boiler
CN109578094A (zh) * 2018-10-07 2019-04-05 联合瑞升（北京）科技有限公司 一种用于供热供汽深度热电解耦的增汽机系统

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US1930456A (en) * 1931-03-25 1933-10-10 Bailey Meter Co Method of and apparatus for heating flowing fluids
US2752899A (en) * 1952-12-30 1956-07-03 Combustion Eng Dual furnace and steam temperature control therefor
GB758833A (en) * 1953-09-30 1956-10-10 Babcock & Wilcock Ltd Improvements relating to forced flow, once-through tubulous vapour generating and superheating units and to a method of regulating temperature of superheat
US2918909A (en) * 1955-09-09 1959-12-29 Sulzer Ag Steam generating and resuperheating plant

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1930456A (en) * 1931-03-25 1933-10-10 Bailey Meter Co Method of and apparatus for heating flowing fluids
US2752899A (en) * 1952-12-30 1956-07-03 Combustion Eng Dual furnace and steam temperature control therefor
GB758833A (en) * 1953-09-30 1956-10-10 Babcock & Wilcock Ltd Improvements relating to forced flow, once-through tubulous vapour generating and superheating units and to a method of regulating temperature of superheat
US2918909A (en) * 1955-09-09 1959-12-29 Sulzer Ag Steam generating and resuperheating plant

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3202135A (en) * 1961-07-27 1965-08-24 Combustion Eng Vapor temperature control method
US3202138A (en) * 1961-07-27 1965-08-24 Combustion Eng Vapor temperature control method

Also Published As

Publication number Publication date
NL229328A (fr)
CH360078A (de) 1962-02-15
GB919262A (en) 1963-02-20
BE579611A (fr) 1959-12-14
FR1224444A (fr) 1960-06-23
NL105665C (fr)

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