US3205664A

US3205664A - Method and means for starting and stopping once-through high-pressure steam boilers

Info

Publication number: US3205664A
Application number: US234158A
Authority: US
Inventors: Nettel Frederick
Original assignee: Individual
Current assignee: Individual
Priority date: 1962-10-30
Filing date: 1962-10-30
Publication date: 1965-09-14
Anticipated expiration: 1982-09-14

Description

Sept. 14, 1965 F. NETTEL 3,205,664

METHOD AND MEANS FOR STARTING AND STOPPING ONCE-THROUGH HIGH-PRESSURE STEAM BOILERS Filed Oct. 30, 1962 1 a-coma M/ZER g A Q I REHEATER r... l r 622 f i f A #50 l s UPER HEATER f 29 i I as F I r C i A 7 EVAPORATDR w i Fug/m5; 151

JTAm -up HmRAuL/c TURB/NE BRAKE 5 55 INVENTOR.

United States Patent 3,205,664 METHOD AND MEANS FOR STARTING AND STOPPING ONCE-THROUGH HIGH-PRESSURE STEAM BOILERS Frederick Nettel, 173 Chapel Road, Manhasset, N.Y. Filed Oct. 30, 1962, Ser. No. 23,l58 9 Claims. (Cl. 6070) The known once-through steam boilers, for example the Benson, Sulzer and more recently the combined ci-rculation type, require for starting and stopping complicated by-pass valve .and tank systems. For starting, their basic purpose is to create a sufficient water and steam flow through the boiler to cool it before the main turbine, normally fed by the boiler, goes into operation. The bypass valves must also go into operation if for some reason steam demand drops suddenly, for example if the steam turbine loses its load by tripping out of the generator it drives.

With increasing boiler outputs the amounts of energy that have to be dissipated in the steam by-pass circuits have reached practically unmanageable values. For example a 900 mw. boiler-turbine set has to dissipate about the equivalent of 150 mw. As expressed by a maker of such boilers: The sheer impact of such requirements puts enormous burdens on the acceptability of supercritical (boiler) design for ever increasing sizes. He continues: In the by-pass system this energy is dissipated in various ways; while a fraction may be utilized in the process, the larger part is transferred to the condenser (of the main turbine). On its way to the condenser, however, dissipation of energy in the form of vibration, noise, radiation, erosion and cavitation is unavoidable. Designers and operators of such systems presenlty in operation have gained thorough respect for the task of handling this energy. (See Combustion April 1962.)

To ease this situation somewhat, it has also been proposed to provide a pump in a pipe short-circuiting the evaporating part of the boiler, consisting mainly of the tubes in the furnace walls, to assist in the cooling of these walls during the starting of the boiler. While this appears a step in the right direction, other equally exposed boiler parts such as the super-heater and reheater remain mostly uncooled. Furthermore, this re-circulation offers little protection in the case when the boiler steam flow more or less suddenly stops, as in the case when the main generator trips out.

A full-size throttle bypass valve system with all accessories therefore remains necessary also in this case, unless safety valves are allowed to open, which is undesirable. This invention aims principally at providing a vastly simplified by-pass system which avoids to a very great extent energy dissipation by throttling of high-pressure steam while recovering a part of its heat regeneratively.

Other and further objects and advantages will become apparent from the following description and the accompanying drawing, which shows in diagrammatic form an embodiment of my invention by way of non-limiting example. The single drawing illustrates a power plant with a once-through reheat boiler supplying a main steam turbine driving an electric generator, the turbine being equipped for using the reheated steam, and a start-up set consisting of a second turbine driving a hydraulic brake during the start-up of the boiler.

The main object of my invention is achieved in a power plant comprising a once-through steam boiler, a first (main) steam turbine, a condenser connected to the exhaust of said turbine, a second (start-up) steam turbine connected to the steam boiler in parallel with the first turbine condensing means connected to the outlet of the second turbine, and a hydraulic brake driven by the secice ond turbine, by the following steps: connecting said second turbine with the boiler during the starting of the boiler, dissipating the mechanical output of said second turbine in said hydraulic brake, condensing the low-pressure steam issuing from the second turbine, heating fluid by leading it through said hydraulic brake, disconnecting said second turbine from the boiler when the steam furnished by the boiler has reached a temperature sufiicient to start the first steam turbine, and starting the latter by admitting steam issuing from the boiler.

Another object of my invention is attained by using the condenser of the first turbine also for the second turbine.

A further object of my invention is realized by using condensate from the condenser as cooling fluid in the hydraulic brake.

Still another object of my invention is achieved by op erating the second turbine with a substantial backpressure, reducing the pressure of the exhaust of the second turbine by throttling before it enters the condenser of the first turbine.

An additional object of my invention is realized by injecting the water heated in the hydraulic brake into the exhaust of the second turbine for cooling it and partly condensing it.

A further object of my invention is attained by leading steam partly expanded in the second turbine through the reheater or reheaters for cooling these parts while the boiler is being started.

Another additional object of my invention is achieved during stopping of the boiler when the steam flow to the first turbine is sharply reduced or stopped, by starting the second turbine in order to maintain a suflic-ient water and steam flow, respectively, through the boiler until it has cooled down.

The second turbine is designed for a steam throughput necessary to cool the boiler components, mostly tubes, sufficiently. Depending on detail design, a steam fiow of between 20 and 30 percent of the boiler full-load flow has been found to be adequate for this purpose. Thus for a boiler of a full-load flow of, say 3,000.000 lbs./h., the second turbine will have to be laid out for a throughput of a-bt. 750.000 lbs./h. If, for example the start-up turbine is designed as backpressure turbine expanding to p.s.i., it may give an output of about 50.000 HP. Such output can be easily dissipated in a high-speed hydraulic brake, which works with condensate as coolant, entering at about 90 F., heating the water to about F. and even more. By returning this water into the feedwater cycle, the heat equivalent of the output of the start-up turbine is regeneratively recovered.

The start-up turbine has to work only during the starting of the boiler which may take place according to local conditions in intervals of several weeks or months. This makes the efficiency of the start-up turbine unimportant and for economic reasons the simplest high-speed design of lowest cost is proper. The start-up turbine also does not need regulating valves, a stop valve being adequate. Under these conditions the cost of the set consisting of the start-up turbine and dynamometer can be expected to be lower than the many extra-high pressures throttle by-pass valves with controlled water injection and drives required in conventional plants, quite apart from the difficulties in operation and maintenance of such valves, as mentioned before.

It is within the scope of my invention to use the lowpressure exhaust of the start-up turbine for creating a cooling steam flow through the reheat section or sections of the boiler during starting of the boiler, and to provide sealing steam to the labyrinth seals of the main turbine and, if so desired, to turn over the main turbine by leading this steam into the low-pressure part of said turbine and then into the condenser before admitting high-pressure steam into it. It is finally also within'the scope of my invention to start a boiler feed pump or other auxiliaries by means of said low-pressure steam before the main turbine can supply such steam. Turning now in more detail. to the drawing, the dotted rectangle shown diagrammatically the once-through boiler 10, with an economizer 11, a reheater 12, a superheater 13, and an evaporator 14. 15 is the high-pressure part of the main steam turbine, 16 its low-pressure part, 17 the main condenser, 48 the main generator driven by the main turbine. 18, 19 and 20 are conventional regenerative feedwater heaters connected to the main turbine, while 21 is a deaerator tank. 22 is the start-up steam turbine, 23 a hydraulic brake driven by the start-up turbine. 25 denotes a low pressure tank. 24 is the main condensate pump, 26 and 27 auxiliary pumps. As shown, the main turbine normally receives steam through pipe 28- Partly expanded steam flows from the outlet of the high-pressure turbine 15 through the pipe 29 into the reheater 12, leaving the latter through the pipe 30 to enter the low-pressure turbine 16 and from there through the pipe 31 into the main condenser 17. The condensate is pumped by the condensate pump 24 via the pipe 32 through the

feedwater heaters

18 and 19 into the deaerator tank 21 and from there via the pipe 33 by the main boiler feed pump 34 through the high-pressure feedwater heater 20 back into the economizer 11.

A pipe 35 with interposed valve 35, branched off from the high-pressure pipe 28, connects with the inlet to the start-up turbine 22. The exhaust from this turbine is in communication with the closed tank 25 through the pipe 36 with interposed valve 37 and throttle plate 38. The tank 25 is further connectedwith'the condenser 17 by means of the valve pipe 39, equipped, if desired, with another throttle plate 38'. During start-up, the hydraulic brake 23 receives condensate from the condenser 17 through the pipe 40 with interposed ,valve 41 by means of the auxiliary pump 26. Heated water leaves the hydraulic brake 23 via the pipe 42 with interposed auxiliary pump 27 and flows into the tank 25. A valved water pipe 43 connects the tank 25 with the de-aerator 21.

Starting of the plant from cold proceeds as follows: After starting .firing and heating up the furnace to suit the particular boiler type, a Water flow is led through the furnace tubes. This flow is provided by a feedwater pump and is, during the initial phase of boiler starting, led back into the condenser. This may be done by the pipe 49, shown dash-dotted, with interposed valve 49a. During this initial stage the pressure in the evaporator and superheater is maintained at a much lower level than the ratedboiler pressure, say at 600 to 700 p.s.i. Soon the water temperature will rise, and when it has reached abt. 500 F., evaporation will begin. In the superheater the steam will be heated to, say 600 to 650 F. This temperature is still too low for the main turbine to start on, but sufiicient to begin operation of the start-up turbine 22. Accordingly, the valve 35 is opened, and while the turbine 22 picks up speed, the hydraulic brake 23 is put into operation by feeding condensate into it through the pump 26, pipe 40 and valve 41.

The expanded steam is led via the pipe36, with valve 37, open, into the closed tank 25 and thence via the pipe 39, with valve. 39' open, into the condenser 17, which under starting conditions may be assumed to be working at near-atmospheric pressure.

As the start-up operation proceeds, the'speed of the boiler feedwater pump 34 is gradually increased. As consequence the pressure of the steam issuingfrom the superheater 13 will raise until the rated boiler pressure of, say, 3500 p.s.i. is reached. This pressure now also prevails at the inlet of the start-upturbine 22 and when it is reached the discharge pressure in pipe 36 will rise to, say, 100 p.s.i. The

throttle plates

38 and 38 before I this pressure to the desired tank pressure and to an acceptable pressure in the condenser.

In conjunction with the rising pressure, the pressure of the steam issuing from the superheater 13, its temperature also rises, but not until it has reached abt. 850 F. or more, can it be used for rolling the main turbine, and during this entire period the start-up turbine 22 has to .remain in operation.

All through this period the hydraulic brake 23 is operating, transforming the mechanicaloutput of the startup turbine 22 into heat by raising the temperature of the water flowing through the brake, the heated water is led into the tank 25.

.There it mixes with the steam coming from the startup turbine 22, condensing it partially or completely. The auxiliary pump 27 interposed in the pipe 42 creates in 25 a water spray for better mixing of steam and water. The valve 29' interposed in the pipe 29a connecting tank 25 with the inlet pipe 29 to the reheater 12, which had been closed so far, is now opened as the steam temperature furnishedby the boiler rises. Low-pressure steam now flows through the reheater 12,'cooling it, and is discharged into the main condenser via the pipes 30 and pipe 44 withvalve 44 open. The water collecting in the tank 25 may be discharged into the de-aerator tank 21 via the pipe 43, with the valve 43' open.

Obviously, While the boiler heats up, all component parts such as the evaporator 14, the superheater 13 and the reheater 12 are cooled by the steam flow through the start-up turbine 22, which can be designed for any desired percentage of the full-load throttle flow of the main turbine. 20 to 30 percent will mostly be satisfactory.

When the steam furnished by the boiler reaches a temperature of about 850 F., the main turbine is connected by opening the valves 23', 29", 30 while the

valves

35', 37, 29, 39', 41, 43' and 44 are closed.

The main steam turbine is now connected to the boiler in the conventional manner, with the feedwater heaters preheating the condensate before it reaches the economizer.

If now for some reason it is necessary to reduce the load on the main turbine more or less suddenly below a point where the reduced steam flow though the boiler just suffices to cool all components exposed normally to very hot boiler gases, the start-up turbine is started, providing the necessary cooling fiow and dissipating the energy no more utilized in the main turbine until the.

boiler has cooled down; the operation of the start-up turbine is substantially thesame as described for starting the boiler.

Contrary to the presently used by-pass and throttling system, the energy dissipation takes place in the start-up set with hardly any vibration, erosion, undue noise and is all the time under complete control of the boiler operator.

Hydraulicbrakes have been found eminently suited for dissipating very large amounts of mechanical energy offered at high rotational speeds. Condensate can be used in these brakes for cooling without danger, of contamination. It is within the scope of my invention to use other fluids in the brake, and to use several brakes where the amount of energy to be handled is very high.

The low-pressure steam in the tank 25 may also be used for providing sealing steam for the glands of the main turbine and it may also be used for turning the main turbine over before it is connected to the boiler.

For this purpose the valve 30 is opened permitting the,

cooling steam, after it has passed the reheater 12, to enter the low-pressure part 16 of the main turbine in which it expands the condenser pressure and drives the main turbine. This is desirable'because it contributes to uniform heating of the rotor of the main turbine when it begins to pick up speed, thereby providing a smoother start. i

Having now described and illustrated my invention, I Wish it to be understood that it is not limited to the special forms and arrangements of parts herein described and shown, or specifically covered by my claims, which follow.

I claim: 1. In the method of starting and operating a highpressure once-through steam boiler forming part of a power plant comprising a main first steam turbine adapted to be connected to the steam boiler, a first condenser with a condensate tank, connected to the exhaust of said first steam turbine, a start-up second steam turbine adapted to be connected to the steam boiler in parallel with said first turbine as regards the 110w of the steam through them, a second mixing type condenser connected to the outlet of the second turbine, a hydraulic brake driven by said second turbine, the steps of:

connecting the second turbine with the boiler during the starting of the boiler while the first turbine is at standstill and not connected to the boiler,

dissipating the mechanical output of said second turbine in said hydraulic brake as heat and leading condensate from said condensate tank of said first condenser through the hydraulic brake to heat said condensate,

condensing the low-pressure exhaust steam issuing from said second turbine at least partially in the second condenser by mixing it with the heated condensate issuing from the hydraulic brake,

disconnecting the second turbine from the boiler when the steam furnished by the boiler has reached a predetermined pressure and temperature,

at the same time starting the first turbine by connecting it to the boiler, and disconnecting the Water flow from the condensate tank of the first condenser to the hydraulic brake.

2. In the method as set forth in claim 1, the step of using the said condenser also as the condenser of the second steam turbine.

3. In the method as set forth in claim 1, the step of operating said second turbine as a back-pressure turbine with a substantial super-atmospheric back pressure, throttling this back pressure and leading the thus throttled steam into the condenser of the first steam turbine.

4. In the method as set forth in claim 1, comprising a boiler with reheater means for steam partly expanded in said first steam turbine, the step of leading exhaust steam from the second turbine into the second condenser for partly condensing it, and leading the uncondensed part into said reheater means.

5. In the method of stopping a high-pressure oncethrough steam boiler forming part of a power plant comprising a main first steam turbine having a condenser connected to its exhaust, a second start-up steam turbine having a mixing type condenser connected to its exhaust, the inlet of said second steam turbine being adapted to be connected to said steam boiler, a hydraulic brake driven by said second turbine, a water supply for the hydraulic brake, the steps of:

stopping the fuel supply to the boiler, then disconnecting the first turbine from the boiler,

at the same time connecting the second turbine with 6 the boiler for starting it and the hydraulic brake driven by it,

feeding water from the said water supply into the hydraulic brake, thereby enabling it to dissipate the mechanical output of the second steam turbine into heat while steam flow through the boiler is maintained for the purpose of removing heat accumulated in the boiler material.

6. A power plant comprising a high-pressure once through type steam boiler, a high-pressure multi-stage first main steam turbine, a first condenser connected to the exhaust of said first turbine, a storage tank for condensate associated with said condenser, a second highpressure start-up turbine, a mixing type condenser connected to the exhaust of said second turbine, a hydraulic brake in driving relation with said second turbine, first valved pipe means connecting the outlet of said boiler with said first steam turbine, second valved pipe means connecting the outlet of said boiler to the second turbine in parallel to said first turbine as regards the steam flow through the said tWo turbines, third pipe means connecting the outlet of the said second turbine with the second mixing type condenser, fourth valved pipe means connecting said storage tank for condensate with the hydraulic brake, fifth valved pipe means connecting the outlet from said hydraulic brake with the second mixingtype condenser, and sixth valved pipe means connecting the said mixing type condenser with said first condenser.

7. A power plant as set forth in claim 6, wherein the boiler includes a reheater for steam partly expanded in said first turbine, the first steam turbine having means to discharge partly expanded steam into said reheater and to receive the reheated steam back before it expands further in said turbine, a seventh valved pipe means connecting the second mixing-type condenser with the reheated for cooling the reheater by steam from the second condenser While the boiler is being started, and an eighth valved pipe means connecting the outlet of said reheater with the first condenser.

8. A power plant as set forth in claim 7, in which the first turbine is provided with a valve in the means connecting the reheater with the first turbine, said valve being so designed that it can be opened While the highpressure part of the first turbine is not connected to the boiler, said valve leading the uncondensed portion of the steam from the second condenser via the reheater into the low-pressure part of the first turbine for turning it over preparartory to connecting the high-pressure part of said first turbine to the boiler.

9. A power plant as set forth in claim 6, in which the second steam turbine is designed to absorb a steam flow of between 10 and 40 Weight percent of the full-load steam flow of the boiler.

References Cited by the Examiner UNITED STATES PATENTS 2,192,759 3/40 Stubbs 60-405 X SAMUEL LEVINE, Primary Examiner.

ROBERT R. BUNEVICH, JULIUS E. WEST,

Examiners.

Claims

1. IN THE METHOD OF STARTING AND OPERATING A HIGHPRESSURE ONCE-THROUGH STEAM BOILER FORMING PART OF A POWER PLANT COMPRISING A MAIN FORST STEAM TURBINE ADAPTED TO BE CONNECTED TO THE STEAM BOILER, A FIRST CONDENSER WITH A CONDENSATE TANK, CONNECTED TO THEEXHAUST OF SAID FIRST STEAM TURBINE, A START-UP SECOND STEAM TURBINE ADAPTED TO BE CONNECTED TO THE STEAM BOILER IN PARALLEL WITH SAID FIRST TURBINE AS REGARDS THE FLOW OF THE STEAM THROUGH THEM, A SECOND MIXING TYPE CONDENSER CONNECTED TO THE OUTLET OF THE SECOND TURBINE, A HYDRAULIC BRAKE DRIVEN BY SAID SECOND TURBINE, THE STEPS OF: CONNECTING THE SECOND TURBINE WITH THE BOILER DURING THE STARTING OF THE BOILER WHILE THE FIRST TURBINE IS AT STANDSTILL AND NOT CONNECTED TO THE BOILER, DISSIPATING THE MECHANICAL OUTPUT OF SAID SECOND TURBINE IN SAID HYDRAULIC BRAKE AS HEAT AND LEADING CONDENSATE FROM SAID CONDENSATE TANK OF SAID FIRST CONDENSER THROUGH THE HYDRAULIC BRAKE TO HEAT SAID CONDENSATE, CONDENSING THE LOW-PRESSURE EXHAUST STEAM ISSUING FROM SAID SECOND TURBINE AT LEAST PARTIALLY IN THE SECOND CONDENSER BY MIXING IT WITH THE HEATED CONDENSATE ISSUING FROM THE HYDRAULIC BRAKE, DISCONNECTING THE SECOND TURBINE FROM THE BOILER WHEN THE STEAM FURNISHED BY THE BOILER HAS REACHED A PREDETERMINED PRESSURE AND TEMPERATURE, AT THE SAME TIME STARTING THE FIRST TURBINE BY CONNECTING IT TO THE BOILER, AND DISCONNECTING THE WATER FLOW FROM THE CONDENSATE TANK OF THE FIRST CONDENSER TO THE HYDRAULIC BRAKE.