US2852003A

US2852003A - Steam heating boiler control systems

Info

Publication number: US2852003A
Application number: US294679A
Authority: US
Inventors: Lawrence C Simmons
Original assignee: NEW YORK CENTRAL RAILROAD CO
Current assignee: NEW YORK CENTRAL RAILROAD CO
Priority date: 1952-06-20
Filing date: 1952-06-20
Publication date: 1958-09-16
Anticipated expiration: 1975-09-16

Description

Sept. 16, 1958 L. c. slMMoNs STEAM HEATING BOTLER coNTRoL sYsTEMs 5 Sheets-Sheet 1 Filed June 20, 1952 o\\ Y O ATTORNEY.

Sept. 16, 1958 L. c. slMMoNs STEAM HEATING BOILER coNTRoL sYsTEMs 5 sheets-sheet 2 Filed June 20, 1952 lum/EN TOR LAWRENCE C. 5\MMON5 ATTORNEY Sept. 16, 1958 l.. c. SIMMONS 2,852,003

STEAM HEATING BOILER CONTROL SYSTEMS ,9g Lan/rence C Simmons, Q .Q m,

ATTOR NEY.

Sept. 16, 1958 L. c. SIMMONS 2,852,003

STEAM HEATING BOILER oNTRoL SYSTEMS Filed June 20, 1952 `1 5 Sheets-Sheet 4 INV ENTOR: Law/'ence GLS/'mm ons,

MLA-Lu,

ATTOR NE Y Sept. 16, 1958 L. c. slMMoNs 2,852,003

STEAM HEATING BOILER CONTROL SYSTEMS Filed June 20, 1952 V 5 Sheets-Sheet 5 T0 FEED LAM/:zama C. 5w. MONS ATTORNEY United States Patent O STEAM HEATING BILER CONTROL SYSTEMS Lawrence C. Simmons, ssining, N.'Y., assignor to The New York Central Railroad Company, New York, N. Y., a corporation of New York Continuation of application Serial No. 184,669, September 13, 1950. This application June 20, 1952, Serial No.294,679

17 Claims. (Cl. 122-443) This invention relates to improvements in steamv heating boiler control systems, and particularly to systems of the type shown in Hamilton and Rowell Patent No. 2,116,943, of May l0, 1938, and my Patent No. 2,566,041, of August 28, 1951, for starting a boiler heater or steam generator of a steam heating or supply system into 'action and controlling and regulating the operation of fuel and water supply pumps for automatically supplying fuel and, if desired, a fuel condition medium, to a burner for heating the boiler and supplying water to the boiler as required according to conditions in the operation of the system. The systems disclosed in these patents are especially designed and adapted for use on an electric or diesel locomotive or on a baggage or other railway car for cooperation with steam standard cars or coaches to supply steam for heating the same, but are also capable of use on other vehicles or in stationary plants where the steam is utilized for either heating or power purposes.

ln the systems covered by the aforesaid patents a blower-motor-turbine-ol-pump set is employed to supply fuel and atomizing air or steam, or both at times, to an atomizing burner, and also to supply combustion air to the combustion chamber or tire-box of the boiler. This blower-motor-turbine-oil-pump set comprises as employed in said patents a gear-type fuel pump, a steam turbine, a paddle-type blower and an electric motor mounted von a common shaft to operate in unison for calibrated fuel and combustion air supplying actions, the set being initially driven by the electric motor to supply fuel and combustion air to start the burner into operation, then operated by the motor and turbine jointly to increase the power and speed of the set when the boiler begins to generate and steam at low pressure is supplied to the turbine to supplement the driving action of the electric motor, and finally operated by the turbine alone under steam supplied thereto at relatively high pressure when the boiler is fully generating. These operations of the blower-motor-turbine-oil-pump set are governed by electrical and pressure-regulated controlling means whereby the electric current to the motor is cut ofi when the boiler pressure reaches a predetermined degree, after which the supply of steam to the turbine to drive the set is regulated and controlled as a function of boiler pressure. In the system shown in Patent No. 2,116,943, combustion air only is supplied to the re-box by the blower of the blower-motor-turbine-oil-pump set while in the system shown in Patent No. 2,566,041 compressed air from a suitable source, such as the main air reservoir of the locomotive, is also supplied directly to the burner for use as an atomizing agent to preliminarily atomize the fuel until steam generation begins, and thereafter, when the boiler begins to generate steam at low pressure, steam is also supplied for admixture with the compressed air passing to the burner to serve as the atomizing agent. As

2,852,003 Patented Sept. 16, 1958 soon, however, as the boiler begins to generate steam at a high pressure, the central means operates to automatically cut off the supply of atomizing air to the burner, and thereafter, as long as the boiler continues in normal operation, steam alone is supplied to the burner as'the fuel atomzing agent.

The systems disclosed in the aforesaid patents differ mainly in the use of atomizing burners of dilferent types for heating the boiler, that of Patent No. 2,566,041 employing an atomizing burner of whirl type and means for controlling the supply of steam and air thereto in Vstarting and running actions and the supply of steam to the turbine in accordance with boiler pressure to govern the boiler firing rate. The boiler control systems of the Hamilton and Rowell patent and my Patent No. 2,566,041 are essentially constant pressure control systems and employ turbine and water pump regulators under control of the tiring rate, which are satisfactory under general conditions and for general service use in controlling boilers operating alone, but have certain disadvantages when the systems are used on Diesel locomotives where the train line pressure is the result of two or three boilers operating in multiple, and it is necessary that each boiler have a ready controllable boiler pressure.

ln my prior application, Serial No. 184,669, led September 13, 1950, now Patent No. 2,767,690 dated October 23, 1956. I have disclosed a boiler control system employing an air-start type of blower-turbine-oilpump set which dispenses with the use of an electric motor as a component part thereof, and which includes novel means for controlling the operation of the turbine and water pump regulators, whereby the disadvantages of the patented systems above referred to are overcome. ln said Patent No. 2,767,690, I have claimed the airstart feature and controlling means associated therewith as a subject-matter of invention. The present application is a continuation-impart of said Patent No. 2,767,690, and the claims thereof cover as a subject-matter of inventionl the novel means above referred to for controlling the operation of the turbine and water feed regulations to govern the boiler tiring rate and the level of the water in the boiler. In this connection it is to be understood that such means for controlling the operation of the turbine and water feed regulators may be used in a system employing blower-turbine-oil-pump sets with or without an electric motor and burners of the types disclosed in the aforesaid patents and application, or of any other suitable types.

The invention will be readily understood from the ,following description, taken in connection with the accompanying drawings, in which:

Fig. 1 is a diagrammatic View of a heating system embodying the novel features of the invention.

Fig. 2 is a diagrammatic view of the wiring of the control circuits thereof.

Fig. 3 is a vertical section on an enlarged scale through the turbine regulator and associated control valve.

Fig. 4 is a longitudinal section on'an enlarged scale through the turbo-fuel pump-blower unit.

Fig. 5 is a vertical section through the Magnatrol oat control device.

Fig. 6 isV a vertical section through one of the magnet valves. f

Fig. 7 is a vertical section through the water pump regulator.

The following legends applying to the general organization shown in Fig. 1 will be of aid in obtaining an understanding of the construction and operation of the parts thereof:

LEGENDS X-Manual valves, even nos. normally open in operation, odd nos. normally closed 11 M F blowoff 13 W C blowol Stack blower M V-Magnel valves MV-1 Fuel MV-Z Turbine air drive MV-3 Train line, may be operated manually MV-4 Continuous blowdown MV-S MV-6 MV-7 Pump on, governed by M F Pump, load control governed by M F Pump off, governed by M F KN-Key needle valves KN-l Continuous blowdown, set for 100 lbs. per hour.

KN-Z Set to keep C I cool KN-3 Set for 40 lbs., when valve 10 is closed and MV-S open KN-4 Low fire, set for minimum fire KN-S High fire, set maximum re KN-6 Open l turn SV or RV-Relef or safety valves SV-l Set for 250 lbs.

SV-Z lSet for 252 lbs.

RV-l Fuel control, set for 40 lbs. RV-2 Pump protection 250 lbs.

PS-Pressure switch es PS-l Set to close at l0 lbs. and reopen at 5 lbs. PS-Z Set to open at 60 lbs. and reclose at 42 lbs.

Pressure regulating valves 1 Atomizer, set for 15 lbs.

2 Turbine standby, set for 15 lbs.

3 Turbine reg. control, set for desired train L. press. MF Magnatrol float, boiler water control CI Cooling jacket, for LW switch LW Low water thermostat WC Water column Referring irst more particularly to the general organization shown in Fig. l, the steam heating supply system comprises a boiler or steam generator A of the type described, an atomizing burner B, herein shown as one of whirl type, a steam driven water pump -WP for supplying water to the boiler, anda fuel-pump-blower unit TPB indicated at 4 in Fig. 1 and shown in detail in Fig. 4, said unit consisting of -a `blower a for supplying combustion air to the 'boiler fire-box, a gear-type pump a' for supplying a liquid fuel, such as oil, to the burner, and a turbine a2 for driving the blower and fuel pump, said blower, fuel pump and turbine being mounted .on a common shaft a3 within a common casing a4; together with a superheated steam service pipe TL for supplying steam to the car heaters, a system of piping connecting the burner, water pump, turbine and fuel pump with the boiler and a source of compressed air supply, a set of devices, generally indicated at WCD, for regulating the water level in the boiler, and an electric circuit C containing control devices associated with automatic control elements in the piping of the system and governing or governed by the automatic control elements in the circuit to regulate the supply of water to the boiler, fuel to the burner, driving air and steam to the turbo-fuel-pumpblower unit, and atomizing air land steam to the burner.

The boiler is provided with two safety valves, one, SV-l, set for 250 lbs. pressure, and the other, SV-Z, set for 252 lbs. pressure, while in the various pipe connections of the system, which are hereinafter more fully described, are arranged a turbine regulator TR indicated at 3 in Fig. l and shown in detail in Fig. 3, and sets of valves and pressure switches for governing the flow of the fluids to the working parts. These sets of valves and switches consist of a set of manual valves 1 to 16, inclusive, and 18, 20, 21, 22, the even-numbered valves being normally open and the odd-numbered valves normally `closed in operation, a set of magnet valves MV-l to MV-7, inclusive, one of which is indicated at 2 in Fig. 1 and shown in det-ail in Fig. 6, a set of key needle valves, KN-l to KN-6, inclusive, a pair of relief valves, RV-l, RV-Z, a set of pressure regulating valves PR', PR-Z, PR-3, and a pair of pressure switches PS-l, PS-2. In addition to these valves and switches, there are arranged at proper points in the piping check valves 17, 17a, 19, 19E, 19h, gauges 19c and strainers 19', the di'- rection of iiow through the check Valves being indicated by the associated arrows and the direction of flow through the strainers being toward their wider ends. Of these valves of set 1 to 16, 18, 20, 21, 22, whose functions are not indicated by legends on or applying to Fig. l of the drawings or hereinafter described, valve 1 is "an emergency valve which may be opened to allow steam to by-pass magnet valve MV3 when occasion requires, valve 3 is a continuousblowdown test valve, valve 5 is `a boiler blow-down valve, and KN-l is la continuous blow-down key-needle valve set for lbs. per hour. Valve MV-S is a magnet valve which may be operated by hand when required. Pressure switch PS-l is set to close at 10 lbs. and reopen at 5 lbs. Pressure switch PS-Z is set to open at 60 lbs. and reclose at 42 lbs. Pressure regulating valve PR-l is set for 15 lbs., while pressure regulating valve PR-2 is set for a turbine standby action at l5 lbs., and pressure regulating control valve PR-3 is set for a desired train line pressure.

Of the set of

valves

17, 17B, 19, 19a, 19", valves 19 may be check valves of conventional type, but valves 17, 17a, 19a, 19b are arranged and designed to perform special functions, as hereinafter described.

Referring now to the `circuit C shown in Fig. 2, which is supplied with current from a battery or other source on the vehicle, this circuit includes the circuit breaker CB, the start button SB, the stop button SB', the start relay coil R-l and its switches R-la, R-lb, the running relay coil R-Z and its switches R-2a, R-Zb, the train line relay coil R-3 and its switches R-, R-3b, the alarm relay R-A, the start control Agastat coil AG-1 30 scc.) and switches AG-la, AB-lb, the arne control Agastat coil AG-Z (15 sec.) and its switch AG-Za, the Magnatrol 9 control Agastat coil AG-S (5 min.) and switch AG-31,

the ignition electrode EL, the ignition set IV, the low water switch LW, the fuel magnet valve MV-l, the turbine air drive magnet valve MV-Z, the train line magnet valve MV3, the blow-down magnet valve MV-4, the pump-on magnet valve MV-S, the pump control magnet Valve MV-6, the pump-off magnet valve MV-7, the llame control switch LS, the burner pressure switch PS-l, the turbine air drive pressure switch PS-Z, the boiler failure light BFL, the Magnatrol oat MF, the train line valve VO (open), the train line valve VC desafios (closed), the upper limit water level switch L-1, the lower limit water level switch 1.-2, and the resistors RES-1 to RES-5, inclusive, of suitable values, which parts are connected to operate in the manner hereinafter described to govern the actions of the water pump, turbo-pump unit and other working parts of the system.

The water supplying connections to the pumpA WP and boiler consist of a supply pipe 21 leading to the pump from a tank 22 or other source of supply and a feed pipe 23 leading therefrom to a condenser 24 and an economizer 25 and thence to the water containing space yof the boiler. The supply of water to the boiler is controlled in this system by regulating the supply of y steam to the pump WP and the water level in the boiler is limited within certain levels by the action of the set of control devices WCD which govern the supply of steam to the pump and also operate to cut lolii' the supply of steam to the pump and ygiven an alarm in the event that the water in the boiler falls below a predetermined low level.

The set of control devices WCD consists of

pipes

26, 27, 28 connected at their upper ends to each other and to the steam space of the boiler and connected at their lower ends to the water containing space of the boiler. In the pipe 26 is arranged the Magnatrol-float boiler water regulator M-F, indicated at 2' in Fig. 1 and (shown in detail :in Fig. 5) controlling the electric switches L-l, L-2, arranged in the control circuit C, while in the pipe 27 is disposed a water column WC and in the pipe 28 is a cooling jacket CJ and a thermostatic low water level switch LW. A pipe 29 containing the key needle valve KN-Z and leading from the intake end of pipe 23, supplies cooling water to the lower end of the jacket, and a pipe 30 allows flow of the hotter water from the top of the jacket to the delivery end of pipe 23, whereby a circulation of cooling water through the jacket is provided for to keep the thermostat inactive as lon-g as the water in the boiler is above the predetermined low level. When, however, the water in the boiler falls below such level, heat from the steam in pipe 28 will energize the thermostatic element to cause it to open switch LW and shut down the boiler.

Leading from the boiler is a main steam supply pipe 31 having a feed branch 32 leading to the water pump drive WPD, a feed branch 33 leading to theturbine a2, a pressure supply branch 34 connecting the branch 33 and the diaphragm chamber of WPR and a feed branch 35 leading to the atomizing burner B for supplying steam as an at-omizing agent thereto. A water pump regulator valve WPR of suitable type and indicated at 7' in Fig. l and shown in detail in Fig. 7, is arranged in pipe 34 between

pipes

32, 33. Spent steam or exhaust pipes 36, 37, leading from the pump WP and turbine a2, are provided for the flow of the exhaust steam therefrom to the jacket of the condenser 24, from which the water of condensation may be conducted through a -pipe 38 back to the water supply tank for re-use. The valve 6 in theY pipe 31 and the valve l0 in the inlet end of pipe 33 are manually operable control valves. Valve 10, however, which controls the flow of steam to the turbineand is arranged ahead of the turbine regulator TR and pressure regulating valve PR-Z in pipe 33, may be auto-4 matically controlled to open when the running relay R-2 is energized. A drain pipe 35 governed by the key needle valve KN-6 and magnet valve MV-7, is included in the steam pipe connections, and drain connections are provided at other points where needed.

The fuel supply connections to the fuel pump and burner consist of a fuel supply pipe 39 leading to the pump a' from a source of fuel supply, an atomizing fuel feed pipe 40 leading from the outlet of the pump to the burner B, a pair of by-pass connections 39 between said pipes across the pump, one of which by-passes contains the high re key-needle valve KN-S set for supply of.' fuel to the burner for maximum re, and the other pump protecting relief valve RV-2, set for 250 lbs., the fuel magnet valve MV1 in the pipe 40, the relief valve RV-l.

in the fuel feed pipe 40, and the key-needle low-fire valve KN-4 in the pipe 40 which by-passes the valve RV-l and is set to control and allow passage of fuel to the burner for minimum fire. The intake end of pipe 39 is provided with a filter and valves of the character indicated.

The air supplying pipe connections of the system consist of a main air supply pipe 4l leading to the pipe 33 from a suitable source of compressed air supply, such as the main air reservoir of the locomotive, a branch pipe 42 leading therefrom to the pipe 34 below the water pump regulator valve WPR, a branch pipe 43 leading therefrom to the turbine regulator TR, and a -branch pipe 44 leading therefrom to the pipe 32, said

pipes

41, 42 and 43 containing the magnetic, the manually operable, the check and key-needle valves indicated. The pipe 44, in which the control valve 9 is arranged, connects with pipe 32 between the control valve 8 and the pump WP and may be employed in case of an emergency to supply cornpressed air to operate said pump when the boiler is not generating and the water therein is too low and must be replenished before the system can be started into action. As stated, the pump regulating valve WPR maybe of any suitable construction and is arranged so as to be governed by pressures in the

pipes

34 and 35 or 42, to regulate the supply of steam to the water pump.

The turbine regulator TR indicated generally at 3' in Fig. l and shown in detail in Fig. 3 with pressure regulator 13R-3, includes a diaphragm chamber 45, arranged between pipes 33' and 43 and a valve chamber 46 arranged in the pipe 33, a diaphragm 47 arranged in the chamber 45 and exposed to the opposing steam and air pressures in the

pipes

33 and 43, a valve comprising spaced valve members 48, 4S in the chamber 46 and controlling the ow of steam to the turbine through upper and

lower ports

49, 49 formed in a partition 46 in the chamber 46, a stem 50 connecting the diaphragm and valve, and a spring 51 acting on the stem to oppose movement of the diaphragm and valve in the downward direction. VSpring 51 is adjustable to regulate its pressure on the diaphragm by means of a supporting and adjusting member 51. The turbine regulator is adapted for cooperation with the pressure regulating valve PR-Z in the by-pass across the valve chamber 46 and the pressure regulating valve PR-3 inthe pipe 43. These valves PR-2 and PR-3 may be of any suitable construction, but, as shown, the valve PR-3 comprises a casing having a diaphragm chamber 52, a diaphragm 53 in said chamber, a spring 54 in the .upper part of the casing exerting downward pressure on the diaphragm, adjusting means 55 for regulating the pressure of the spring, locking means 56 for locking the adjusting means in adjusted position, a valve chamber 57 beneath the diaphragm having inlet and outlet ports 5S and 59, a partition 60 separating said ports from each other, a port 61 connecting the inlet port with the bottom of the diaphragm chamber, a port 62 connecting the outlet port with the bottom of the diaphragm chamber, a valve 63 in the valve chamber, a stem 64 connecting said valve with the diaphragm, and a spring 65 pressing upward on the valve to hold it closed or more or less open against the pressure of the spring 54. Valve PR-2 may be generally similar in construction to valve PR-3. The function of valve PR-3 acting in conjunction with the turbine regulator valve TR is to control the turbine action for a desired normal train line pressure, while the function of valve PR-Z, which is set for 18 lbs., is to control the stand-by action of the turbine. The atomizer pressure regulating valve PR-l is normally set for 15 lbs. pressure.

lt will be understood that when the system is in running operation the diaphragm 47 is subjected on its upper side to the pressure of the steam at a desired boiler pressure and on its lower side to the counteracting pressure of the compressed air passed by valve member 63 of valve PR-,S plus the pressure of the spring 51. Normally the air in pipe 43 at the inlet side of the valve PR-S is at main reservoir pressure, e. g., 1,30 lbs. per sq. inch, from which it may be varied by regulation of the spring 54 and position of valve member 63 to deliver the air at any desired pressure 'below or up to 136 lbs. to the diaphragm chamber 45 to control the movements of the diaphragm 47, and consequently the normal positions and movements of valve members 48, 48', to regulate the ow of steam to the turbine as a function of boiler pressure to drive the turbine at a desired substantially uniform speed, whereby the amount of fuel supplied to the burner is automatically controlled to cause the boiler to generate steam at the desired maximum pressure. Through the adjustment of valve PR-3 the boiler pressure may be changed to any pressure within the limits of the main reservoir air pressure, in this instance, for example, from 250 to 120 lbs. Valve Pit-2 operates to pass sufficient steam to the turbine to keep the turbine running for stand-by tiring when the turbine regulator valve is closed.

In the air starting operation of the system, assuming that the boiler is cold and in starting condition, and with all even numbered valves, except Nos. 4 and lO open and all odd numbered valves closed, the starting button is pressed with the result that valves MV-l and MV-2 are opened for the ow of air to the turbine to drive unit TPB and for the flow of oil to the burner. Valve 20, which is a reducing valve located on the turbine side of valve NIV-2, is preadjusted to allow about 25 lbs. pressure on the turbine when valve MV-Z is open to about 130 lbs. main reservoir pressure. The check valve l5 following valve Ztl is to protect the air line from condensation llow from the steam line as a safety precaution, although the normal pressures existing in the system could only cause a flow to exist from the air line towards the turbine. The turbine regulator valve TR is normally wide open until the steam pressure in the pipe line 33 is approximately 100 lbs. or more. As this valve and the regulating valve PR-2 are not concerned in the air start, except as above described, their working functions at this stage need not be considered. When the fuel supplied to the burner ignites, however, turbine valve is opened. The turbine and burner atomizer will run on air only until the boiler pressure is suicient to lift the check valves in the steam supply pipes, at about 2S lbs. Thereafter, both steam and air will be fed to the turbine and burner until at about 50 lbs. boiler pressure switch PS-2 will be opened and cause magnet valve MV-Z to close. This cuts olf the air supply to the turbine and burner and the steam supply pipes will be supplied with steam to drive the turbine, furnish atomizing steam to the burnerand operate the'other parts of the apparatus. If the boiler is to be started when the steam pressure is up, the same operation as above described is followed, but-in this case when valve 10 is opened the air start magnet valve MV-Z will close almost immediately. In the normal air starting operation valve MV-2 is energized and opens whenever pressure switch PS*2 is closed or start control Agastat AG-1 is energized. The interlock on AG-1 in MV-2 circuit will keep MV-2 open for 30 seconds after the start button is pushed, regardless of the boiler pressure and switch PS-2 will keep MV-2 open until the gas pressure in the pipe line to the burner atomizer reaches a predetermined amount Suthcient to keep the turbine running at the desired maximum speed. Whenever switch PS-Z is open and AG-l has been deenergized for over 30 seconds MV-2 is closed. As soon as the system begins to run entirely on steam generated by the boiler, the turbine regulator is governed by boiler pressure to regulate the speed of the unit TPB and the amount of fuel supplied thereby to the burner and the amount of combustion air supplied to the boiler rebox per unit of time to keep the boiler generating at the desired rate.

As before stated, check valve Y19a in pipe 33 between valve 10 and pipe 32, and check valve 19'D in pipe 31 adjacent the boiler, have special functions. Valve i7 is a cheek valve and acts only to protect against any back flow of steam into Ythe locomotive air brake system air. The arrow beside valve 17 in Fig. l shows direction of flow through the valve.

Valve V17 is mechanically similar to 17 except that a small hole is drilled through the valve seat and its function is thereby materially changed. When magnet valve .lV-5 is opened, air flows through valve l' through throttling valve KN-3 to chamber of WPR. Now, ii valve 17a had no hole in its seat, the air pressure in chamber WPR would build up to the maximum pressure of the locomotive air system and WPR would be forced to the fHV open position regardless of steam pressure throng4 sf-6. lf valve 17a had a large hole in its seat, as compared to orice in 14N-3, the air flow from MV-i through KN-3 would not be able to add to the pressure in chamber of NPR and WPR would still be entirely controlled by steam pressure through MV-(i. As designed, however, valve E75 has a small hole in its seat and thereby allows the air pressure to add to the steam pressure in chamber of WPR.

Now the benefits of such an arrangement can be shown by the following examples. Assume the boiler is idling on the line and little or no steam is flowing through valve 2. The steam pressure in line 33' is only suflicient to supply fuel and air for this purpose and perhaps is at 2i) lbs. pressure. WPR is set nominally to supply steam to the boiler water feed pump at an equivalent rate but say it is slowly falling behind in its supply. When l\/lv'-S opens an account of this lowering of water in the boiler` the air passing through KN-S will bleed olf through valve 1!a and the chamber pressure in WPi will only build up to say 36 lbs. under this dynamic condition. With 35 lbs. of pressure in chamber, the boiler feed steam will be increased but not to a maximum rate which would be the case except for valves i7t and Kl 3.

A maximum feed water rate is not good for the boiler for reasons well known and also may cause a drop in boiler pressure which would cause the controls to iucrease the fuel-air rates and tend toward a cycling condition. lt will be noted that in each case of increase in boiler load the air pressure will add to the steam pressure from line 33 until line 33 is at the same pressure as the locomotive air system. ff/PR is fully opened at pressures somewhat under the pressure of the locomotive air system.

The chamber of valve WPR is under atmospheric air pressure only when the water in the boiler is higher than desired; at this time valve MV5 is closed and ivlV-' is opened. When boiler water level is at nominal desired range, then the chamber of WPR is under the steam pressure obtained from line 33 through valve MV-t; MV- and MV-S being now closed. When the boiler water level is below the desired level, then valve MV-i opens and loads in unison with the steam pressure from line 33, the chamber of WFH. The amount of pressure added by the air to chamber of WPR at this time will be in an inverse proportion to the firing rate, being zero lbs. when the pressure in line 33 is at a maximum tiring rate amount of say lbs., and say l5 lbs. when the pressure in line 33 is at a minimum tiring rate cf perhaps 20 lbs. Valve Pit-3 is provided to regulate the air pressure supplied to the turbine regulating valve 46. Valve 19a, provided with a /w hole in its seat, operates to keep pipe 32 leading to the water pump from being immediately charged with air when valve lil is opened, which would decrease the pressure in the burner atomizing line and shut down the boiler by opening switch PS-l in the running relay circuit` It also limits the air ow to the Water pump in the event that the pump regulator' valve WPR is open. This valve automatically closes during the start period, although it may remain open for a few minutes. The check valve 19h operates to keep the air from charging the boiler. lt is also very necessary to keep low pressure, low temprature steam from entering the steam line and condensing in the atomizing line to the burner. The air pressure on top of this check valve holds it closed until the boiler pressure is approximately 25 lbs. Thereafter, there is a steady and increasing ow of steam to the turbine and atomizer. As stated, the water pump regulator WPR may be of any suitable construction, but I prefer to use one of the type indicated at 7 in-Fig. l and shown in detail in Fig. 7. This regulator, which is somewhat similar in construction to the turbine regulator TR, is4 interposed between

pipes

32 and 34 and comprises in its construction a diaphragm casing 66 having arranged therein a exible diaphragm 67 dividing the casing into upper and

lower chambers

68 and 69, chamber 68 being open to the atmosphere while chamber 69 is in communication with pipe 311i above the level of

pipes

35 and 42. Above the diaphragm casing is a valve casing 70 communicating with portions of the steam supply pipe 32 and having a partition provided with a port 71 controlled by a valve 72 carried by a sliding stem 73 which couples the valve to the diaphragm. The stem is slidably mounted in a frame structure connecting the diaphragm and valve casings and consisting of a pair of rods 74 connected at their lower ends to the diaphragm casing and at their upper ends to each other by a head 75 connected by a tubular guide coupling 76 to the valve casing. The stem 73 is slidable through the head 75 and coupling 76 and also through an adjusting member 77 which is slidably mounted on the rods toward and from an abutment 78 on the stem, between which abutment and the member 77 is arranged a supporting and pressure controlling spring 79. The spring normally holds the member 77 pressed upward against adjusting nuts engaging threaded portions 8l of the rods, by which the member 77 may be adjusted to regulate the pressure of the spring and its resistance to the upward movement of the stem and valve under the pressure on the diaphragm of uid in the diaphragm chamber 69. With this arrangement the regulator WPR controls the supply of steam to the feed water pump WP to govern its action. Normally the valve 72 is held closed when the pressure in the diaphragm chamber 69 is zero and opens according to the steam pressure in the diaphragm chamber 69 supplied thereto from pipe 34 connected to the turbine inlet pipe 33. By connecting the diaphragm chamber 69 to the turbine inlet pipe 33 through pipe 34 the diaphragm pressure will be automatically varied according to turbine speed, since the regulator WPR allows more steam to pass to the feed water pump proportionately as the firing rate increases. This method of operation requires the use ot controls to definitely limit 'the water in the boiler within certain levels. This is done through the use of the iloat MF controlling upper and lower water limits electric switches L-i and L-Z. With 'the boiler level normal, between one-halt` and threevalve Niv-7 which opens and bleeds off all the pressure from the pump regulator diaphragm chamber. The boiler water level will then start t-o lower and at about three-quarters of a glass switch L-l returns to its former position and the feed pump again operates.

lf the pump regulator adjustment is such that the boiler water level was lowering from the normal position then switch L-2 would energize magnet valve M-S and open the circuit to Magnatrol control Agastat AG-3. Time delay switch L-Z will hold its interlock in the closed position for tive minutes after the coil is deenergized. At the end of this live minute period the interlock on AG-3 will open the circuit to the running relay R-2 and shut down the boiler. However, in the tive minute interval MV-S again opens and, through a presetting of 14N-3 against the 1/16 inch hole in check valve after MV-6, about '60 lbs. of additional pressure from the air supply pipe 4l will be placed in the pump regulator diaphragm chamber. This opens the pump regulator valve '72 and speeds up the pump. The water level then returns to normal in about two minutes and switch L-Z will return to its normal position.

ln this system, as stated, the feed of water to the boiler is controlled by controlling the supply of steam to the water pump driver WPD. By connecting the diaphragm chamber of the pump regulator to the turbine inlet pipe the diaphragm pressure regulates the pump speed with the iiring rate and as the rin-g rate increases the water pump regulator allows more steam to feed to the water feed pump. The Magnatrol oat switch M-F is a oat mounted in such a manner on the boiler as to maintain a position in direct relation to the height of water in the boiler through that section of the boiler corresponding to the section covered by the boiler water glass. The Magnatrol float operates by magnetic action the two single pole double throw switches Irl and L-2 which are displaced from each other by about one inch in a vertical direction and operates as follows: With no water in the boiler or water below the middle of the water glass the switch positions are as shown in Fig. 2. The feed pump may be operated on air or steam until the water level in the boiler is at the normal operating level. At this stage switch L-l is as shown in Fig. 2, but switch L-2 completes the circuit to AG-S. This is a time delay relay having immediate action when coil AG-3 is energized but having a tive minute delay when the coil AG-3 is deenergized. In this normal operating position MV-6 and AG3 are both energized ACT-3 interlock in the R-2 or running relay circuit is closed and MV-6, a magnet valve, is open. As previously described the turbine regulator controls the steam to the turbine in accordance with boiler pressure, varying the pressure to the turbine in approximately the inverse ratio to boiler pressure, and thus controlling the boiler iiring rate. With MV6 open the pump regulator WPR iS under the inuence of the tiring rate, opening as the rate` is increased and closing as the rate is decreased.

With an ideal condition, this arrangement could keep the boiler water level constant,` but such a condition is not obtainable in practice, and the boiler level will either rise or fall. lf the boiler water level rises switch L-l will be opened to break the circuit to MV-6 and energize magnet valve MV7. When this occurs the pump regulator diaphragm pressure is discharged to atmosphere and the steam to the feed pump is shut oii'. As the water level decreases the normal operating condition is again obtained, as above described, wherein the pump regulator WPR is opened as a function of the iringrate. If the water level falls too far switch L-Z will operate to open the circuit to AG-3 and complete the circuit to magnet valve MV-S located in the pipe 42 between the locomotive main air reservoir (not shown) and the diaphragm of the pump regulator WPR. This pipe contains the key metering needle valve KN-3 which is set to obtain 40 lbs. pressure on the regulator diaphragm when the turbine pressure is zero. The small hole, l" diameter, in the seat of check valve 17EL allows some leak-oi and under this condition the key needle-valve KN-3 can be set to control the air pressure on the pump `regulator diaphragm at any pressure between 0 lbs. and

a few pounds below main air reservoir pressure. Now with the pressure set at 40 lbs. against 0 lbs. in the turbine, the two pressures will rise approximately together; in other words, if the turbine has 20 lbs. pressure, the diaphragm will be under 60 lbs. pressure during periods of low water. The full pressure from the air line is not desired, but only enough pressure to speed the pump up a fair amount over its speed at the normal water level setting. A wide open feed pump valve MV-S would accelerate the pump too fast, at low ring rates, and cause erratic boiler operation on account of dumping a lot of cold water in the boiler in a short time. lt would also affect the efficiency of the turbine steam condenser, as there would be periods when the amount of feed water would not be sufficient to condense the steam.

The action of the time delay relay AC1-3 is as follows: When its circuit is opened it will hold the interlock in series with the running relay R-Z in closed position for ve minutes. lf in that time the boiler water level has not returned to the normal operating level the interlock will open the circuit to R-Z and shut down the boiler. Thus AG-S will prevent operation of the boiler if the water level continues below about one half water glass for more than live minutes, and will prevent starting the boiler if there is insufficient water in the boiler. lt thus works in conjunction with LW, the temperature con trolled water switch, giving an additional safety factor for normal operation and adding the feature of preventing damage being done to the boiler on account of being tired without sufficient water.

As before stated, the boiler pressure control in the patents referred to is essentially a constant pressure con* trol. This type of control is satisfactory for boilers operating alone, but on diesel locomotives, the steam train line pressure is the result of two or three boilers operating in multiple, and hence it is necessary that each boiler have a. readily controllable boiler pressure which is obtained by the action of the turbine regulator operating in conjunction with the pressure controlled means and the pump regulator to control the firing, Water feed and generating ratios. The lower diaphragm chamber of the turbine regulator is preloaded with air pressure varying from -125 lbs. p. s. i. The spring in the turbine regulator valve is set to close when the steam pressure is 125 lbs. in the top diaphragm chamber and there is 0 lbs. air pressure in the bottom chamber. The air pressure in the turbine regulator regulating valve is adjusted by regulating valve PR-3 to give the desired boiler pressure according to the pressure gauge connected to the bottom diaphragm chamber. This gauge is calibrated to show 125 lbs. pressure at the normal zero position of the gauge hand. Thus when air pressure at 70 lbs. is added to the 125 lbs. spring pressure 195 lbs. pressure in the boiler will be required to close the turbine regulating valve and reduce the tiring rate to a point where it will just maintain standby losses. By adjusting the air pressure supplied through control valve PR-3, the steam pressure in the boiler can be controlled from 125 libs. to approximately 265 lbs., assuming a main air reservoir pressure of 140 lbs., and thus the steam pressure can be raised and lowered as desired by the operation of control valve PR-3.

From the foregoing description, taken in connection with the drawings, the construction and operation of the system will be understood without a further and extended description, and it will be seen that the invention provides novel means for regulating the action of the water feed pump and controlling the level of the water in the boiler, and pressure controlled electrical means for governing the action of the working parts of the system in a simple, reliable and efficient manner to control the tiring and Water feed rates to govern the steam generating action of the boiler so that boilers operating in multiple will supply the desired steam train line pressure. While the construction disclosed is preferred, it will, of course, be un- 12 derstood that changes in the form, arrangement and the details of construction of the parts may be made within the scope of the appended claims without departing from the spirit or sacrificing any of the advantages of the invention.

Having thus described my invention, l claim:

l. A steam generation plant, comprising a boiler, a burner for heating said boiler, a source of compressed air, an air or steam driven pump for supplying fuel to said burner, steam and air lines leading respectively from said boiler and from said source of compressed air to the pump, a regulator responsive to boiler pressure for governing the supply of steam to said fuel pump, and thus the tiring rate of said burner, an air or steam driven pump for supplying water to said boiler, a regulator responsive to the pressure of steam supplied said fuel pump for controlling the supply of steam to said water pump, a compressed air conduit connected with said fuel pump regu lator for varying the action of said fuel pump regulator to render said fuel pump regulator responsive to a boiler pressure of a desired degree and thus to regulate the tiring rate in accordance with the desired boiler pressure, and valve means in the air and steam supply lines for con trolling the feed of air and steam to said pumps to adapt the pumps to be driven by air in a starting action and to be driven by steam when the boiler generates steam at a predetermined pressure.

2. In a steam generator, 1a boi-ler, a burner for heating the boiler, a pump for supplying fuel to said burner, a steam drive means for driving said fuel pump, a regulator for governing the supply of steam to said fuel pump drive means, a source of water, a pump for supplying water to said boiler from said source, a water pump motor, and a regulator governing the supply of steam to said water pump, said first regulator being inversely responsive to variations in the boiler pressure to control the rate of fuel supply to said burner, and, thus, the firing rate of said 4burner inversely to the boiler pressure variations, and said second regulator being responsive to variations in the pressure of the steam supplied said fuel pump drive means whereby the rate of water supply to said boiler is varied directly in accordance with the firing rate of said burner.

3. A steam generator according to claim 2, and in which 1a float is located in said boiler, additional water supply regulating means under the control of said oat to further regulate the supply of water to said -boiler inversely in dependance on the height of the water level therein.

4. A steam generator according to claim 3, and in which said additional water supply regulating means comprises a valve and electrical switch means influenced by the position of said float in said boiler for controlling said valve.

5. In a steam generator, a boiler, 1a burner for heating said boiler, a pump for supplying fuel to said burner, steam driven means driving said fuel pump, a regulator directly responsive to boiler pressure for governing the supply of steam to said fuel pump driving means, and, thus, the fuel supplying action of said pump, thus, to regulate the firing rate of said burner, said fuel supply regulator including variable resistance means acting inversely to the boiler pressure, a source of water, a water pump for supplying water to said boiler from said source, a pump driving said water pump, a regulator responsive to the pressure of the steam supplied said fuel pump drive means for governing the rate of supply of water to said boiler directly in accordance with the burner tiring rate.

6. In a steam generator, a boiler, a burner for heating said boiler, a pump for supplying fuel to said burner, steam driven means driving said fuel pump, a regulator governing the supply of steam to said burner, a regulator governing the supply of steam to said fuel pump drive means to control its speed and the rate of supply of fuel to said burner, a source of water, a water pump for supplying water to said boiler from said source, a steam driven motor driving said water pump, a regulator for governingv the supply of steam to said water pump motor, thus, to control its speed, a source of constant pressure compressed air, a connection between said compressed air source and said fuel pump drive means regulator, said last-mentioned regulator being responsive to boiler steam pressure and said compressed air pressure acting oppositely to the steam pressure to increase the supply of steam for driving said fuel pump faster when the steam pressure is relatively low, thus, to increase the firing rate of the burner, said water supply regulator having a connection with the steam supply to said fuel pump drive means for acting to increase the supply of steam to the water pump, and, thus, the supply of Water to the boiler in accordance with the firing rate of the burner.

7. In a steam generator, a boiler, a burner for heating the boiler, a pump for supplying fuel to said burner, steam driven means driving said fuel pump, a regulator for governing the supply of steam to the fuel pump drive means, a source of water, a pump for supplying Water to the boiler from said source, a steam driven motor driving said water ptunp, a regulator governing the supply of steam to the water pump drive motor, said first regulator being responsive to variations in the boiler pressure to control the rate of fuel supply to said burner, and, thus,

vthe ring rate of said burner inversely to the boiler pressure variations, and said second regulator being responsive to variations in the pressure of the steam supplied said fuel pump drive means, whereby the rate of Water supply to said boiler is varied directly as the firing rate of said burner, and means controlled by the level of Water in said boiler for altering the effect on said water pump regulator of the pressure of steam supplied said fuel pump drive means, to cause the speed of said water pump to vary inversely to the height of level of said boiler water.

8. A steam generation system comprising a boiler, a burner for heating said boiler, a pump for supplying fuel to said burner, steam drive means for said pump, a conduit connecting said pump drive means with said boiler to supply steam to said pump drive means, a fuel pump regulator having steam control means connected in said fuel pump drive means steam supplying conduit, said fuel pump regulator being connected to said boiler and being responsive to the boiler steam pressure to reduce the supply of steam to said fuel pump drive means as the steam pressure increases, and, thus, to reduce the ring rate of said burner, a source of Water, a pump connected to supply water to said boiler from said source, a steam driven motor driving said Water pump, said water pump drive motor having a steam supply conduit from said boiler, a Water pump drive motor regulator having a connection to said fuel pump drive means steam. supply conduit, and having steam control means in said Water pump drive motor steam supply conduit, said regulator operating said water pump steam control means to increase the supply of steam to said pump, and, thus, increase the supply of water to the boiler directly in accordance with the pressure of the steam supplied said fuel pump drive means, so that the water is supplied directly in accordance with the firing rate of said burner, a steam control Valve connected in said connection between said water pump drive motor regulator and said fuel pump drive means steam supply conduit, means including an electric circuit for controlling said Valve, and means for altering said electric circuit in dependence on the height of the level of the water in said boiler.

9. A steam generation system comprising a boiler, a burner for heating said boiler, a pump for supplying fuel to said burner, a motor drivingly connected with said fuel pump, a conduit supplying steam from said boiler to said pump motor driving said fuel pump motor, a fuel pump regulator having steam control means connected in said fuel pump motor steam supplying conduit, said fuel pump regulator being connected to said boiler and be- '14 ing responsive to the steam pressure therein to reduce the supply of steam to said fuel pump motor as the boiler steam pressure increases, and, thus, to reduce the firing rate of said burner, said regulator means being responsive to a pressure condition which varies directly as the boiler pressure for closing said conduit when a predetermined maximum boiler pressure is reached, a second conduit means by-passing said regulator and supplying a small amount of steam to said fuel pump motor when said regulator closes said first-mentioned conduit, a source of water, a water pump connected to supply water to said boiler from said source, a steam driven motor connected for driving said water pump, said Water pump motor having a steam supply conduit from said boiler, a water pump motor regulator having steam control means in said water pump steam supply conduit, said water pump motor regulator having a connection to said fuel pump steam control means, said Water pump motor regulator operating said water pump steam control means to increase the supply of steam to said pump, and, thus, the supply of water to the boiler directly in accordance with the pressure of the steam supplied said fuel pump motor, so that the Water is supplied in accordance with the firing rate of said burner, a steam control valve connected in said connection between said water pump regulator and said fuel pump motor steam supply conduit, and means responsive to the level of water in the boiler for exercising further control of the supply of steam to said water pump to cut off the supply of water when the boiler water level rises above a predetermined maximum.

10. A steam generation plant, comprising a boiler, a burner for heating said boiler, a pump for supplying fuel to said burner, a motor for driving said pump, a regulator responsive to boiler pressure for governing the supply of steam to said fuel pump motor, and, thus, the fuel supplying action of said fuel pump, thus, to regulate the firing rate inversely to the boiler pressure, said regulator being responsive to a predetermined maximum boiler pressure to cut olf the supply of steam to said fuel pump motor, a water pump having a steam driven driving motor, a regulator responsive to the pressure of the steam supplied said fuel pump motor for normally controlling the supply of steam to said water pump motor to maintain a given normal level of water in said boiler,

and means controlled by the level of water in the boiler and connected to said water pump motor regulator to adjust the supply of steam to said water pump motor and, thus, selectively to adjust the speed of said pump to decrease said speed when the water in the boiler rises above the normal water level limits and to increase said speed when said level falls below the normal level limits.

1l. A steam generating plant, comprising a boiler, a burner for heating said boiler, a pump for supplying fuel to said burner, a steam driven motor driving said fuel pump, -a regulator inversely responsive to boiler pressure for governing the supply of steam to said fuel pump motor, means varying the action of said fuel pump regulator to render it responsive to a boiler pressure of a desired degree to stop said supply of steam to said pump, and, thus, to regulate the ring rate of said burner inversely to the boiler pressure to maintain the desired boiler pressure, a pump for supplying water to said boiler, a steam driven motor driving said water pump, a regulator responsive to boiler pressure for normally controlling the supply of steam to said water pump, thus, to maintain a predetermined normal level of water in the boiler, an electric circuit, including an electromagnet, a' valve in said water pump regulator steam supply controlled by said electromagnet for selectively controlling the action of said water pump regulator, and, thus, the speed of the water pump to decrease said pump speed when the Water in the boiler rises above the normal level, and to increase said pump speed when said water level in said boiler falls below the normal level, and a float controlled switching means controlling the action of said valve.

12. A steam generator` plant, comprising a boiler, a burner for heating said boiler, a fuel pump for supplying fuel to said burner, a motor for driving said pump, a regulator inversely responsive to boiler pressure governing the supply of steam to said fuel pump motor, and thus, the fuel supplying action of said-pump, and, thus, regulating the firing rate, means varying the action of said regulator to render it responsive to a predetermined maximum boiler pressure to shut olf said supply of steam to said motor, a water pump having a steam driven motor, a regulator responsive to the pressure of steam supplied said fuel pump motor for controlling the supply of steam to the Water pump motor to maintain a predetermined normal level of water in said boiler, an electric circuit, a magnet valve connected in said circuit and controlling the supply of steam, and, thus, the action of said Water pump regulator, to reduce respectively, the supply of steam to the Water pump motor when the level rises above the normal water level and increase the supply of steam to the Water pump motor when the Water level falls below the normal level, a oat in said boiler, switching means controlled by said Float governing the action of said valve.

13. A steam generation plant, comprising a boiler, a burner for heating said' boiler, a pump for supplying fuel to said burner, a motor for driving said fuel-pump, a regulator inversely responsive to boiler pressure governing the supply of steam to said fuel pump motor, a nd, thus, the .fuel supplying action of the pump, thus, to regulate the tiring rate of said burner, means for varying the action of said regulator to render it responsive to the desired maximum boiler pressure, to cut oil said supply of steam to said motor, a Water pump, a steam driven motor driving said Water pump, a regulator responsive to the pressure of the steam supplied said fuel pump for controlling the supply of steam to said water pump motor, thus, to maintain a given normal level of water in said boiler, an electric circuit, a valve connected in said electric circuit to be controlled thereby for controlling the action of the water pump motor regulator to reduce respectively, the supply of steam to the water pump motor when the water level rises above the normal Water level and increase the supply of steam to said water pump motor when the water level falls below the normal level, a valve r'or cutting olf the supply of fuel to the burner in the event that the normal level of the water is not ret red within a given period after its fall to a low level, a iloat in said boiler, and switches in said circuit controlled by said loat governing the operations of said valve.

14. A steam generation system comprising a boiler, a burner for heating said boiler, a 4fuel pump supplying fuel to said burner, a fuel pump motor drivingly connected with said prunp, a conduit connecting said pump motor with .said boiler to supply steam to said pump motor, a fuel pump motor regulator having steam control means connected in said fuel pump motor steam supplying conduit, conduit means connecting said fuel pum-p regulator to said boiler, said regulator being responsive to the pressure of the boiler steam to reduce the supply of steam to said fuel pump motor as the boiler steam pressure increases, and, thus, to reduce the tiring rate of said burner, a source of Water, a water pump connected to supply water to said 4boiler from said source, a steam driven water pump motor connected to drive said Water pump, said Water pump motor having a steam supply conduit from said boiler, a water pump motor regulator having a connection to said fuel pump motor steam supply conduit and having steam control means in said water pump motor steam supply conduit, said water pump regulator operating said IWater pump motor steams control means to increase the supply of steam to said water pump motor, and, thus,` the supply of Water to the boiler directly in accordance with the pressure of the steam supplied said fuel pump motor so that the Water 4is supplied in accordance with `the tiring rate of said burner, and means governing the action of said Water pump motor regulator and operative at subnormal level of the water in said boiler to speed up said water pump for a given period of time and to shut down the burner if the normal water level is not restored during such time period.

l5. A steam generator system comprising a boiler, a burner for heating said boiler, a fuel pump for supplying fuel to said burner, a steam driven fuel pump drive means, steam conduction means for `supplying steam from said boiler to said fuel pump drive means, a regulator comprising a diaphragm operated valve connected in said steam conduction means for governing the supply of steam to said fuel pump drive means, a steam driven pump for supplying `Water to the boiler, a steam conduit for supplying driving steam from said boiler to said water pump, a regulator comprising a diaphragm operated valve connected in said water pump steam supply conduit for governing the supply of steam to said Water pump, conduit means connecting the diaphragm of said fuel pump drive means regulator with the boiler steam, said fuel pump regulator diaphragm being operatively connected to said fuel pump regulator valve to tend to close said fuel pump regulator valve as lthe steam pressure increases, thus, to reduce the burner tiring rate oppositely to the steam pressure, and conduit means connected with said water pump regulator diaphragm and with the steam supply conduction means of said fuel pump drive means at a point toward said fuel pump drive means from its regulating valve, to control the operation of said water pump directly in accordance with the `supply of steam to said fuel pump drive means, thus, to regulate the supply of water to said boiler directly in accordance with the tiring rate of said boiler.

16. A steam generation system according to claim 15, and a source of constant pressure compressed air, conduit means connecting said compressed air with the side of said diaphragm of said fuel pump regulator opposite from the stem connected side, thus, to set said regulator to Iclose the supply of steam to said fuel pump at a predetermined boiler steam pressure sufficient to overcome all forces, including said compressed air acting on said diaphragm, in opposition to said steam pressure on said diaphragm, and means for regulating the pressure of the air supplied said fuel pump regulator.

17. A steam generation system according to claim 15, and in which supplemental control means is provided for governing the action of said diaphragm of the water pump regulator at normal water levels in the boiler to increase or decrease the speed of said -vvater pump at low and high water levels, respectively.

References Cited in the tile of this patent UNITED STATES PATENTS 2,116,943 Hamilton et al May l0, 1936 2,204,138 Knowlton June 1l, 1940 2,235,541 Warren Mar. 18, 1941 2,566,041 Simmons Aug. 28, 1951