Основой является цветной OLED-дисплей с разрешением 128х128 точек размером 1,5 дюйма с контроллером SSD1351. Этот дисплейный модуль можно легко найти в продаже, он имеет интерфейс SPI по умолчанию, но для настройки параллельного интерфейса нужно только припаять несколько резисторов R8 и R10-R7 и R9. Параллельное управление в сочетании с микроконтроллером ATxmega256A3U и частотой тактирования 32MHz, обеспечивает быстрое обновление экрана.

Arduino Ublox GPS: So this Lazy Old Geek (L.O.G.) was looking for a GPS for an Arduino project. Well, I found this UBLOX-NEO-6M GPS on ebay: http://www.ebay.com/itm/Ublox-NEO-6M-GPS-Module-with-EEPROM-and-Built-in-Active-Atenna-APM2-5-APM2-0-Com-/251548034492?pt=LH_De…

Схема зарядного устройства для герметичных свинцовых (гелевых) аккумуляторов

Description Oct. 9, 1951 N. c. PRICE FUEL coNTRoL sYs'rEu FOR TURBO POWER PLANTS 2 Sheets-Sheet l Original Filed March 6, 1942 .ntv n te Nv INVENTOR NATHAN C. PRlcE BY Agent Oct. 9, 1951 N. c. PRICE 2,570,591 FUEL CONTROL SYSTEM FOR TURBO POWER PLANTS y Original Filed March 6, 1942 2 Sheets-Sheet 2 l Ef 27 39 38 lm'rlou l2 STARTER 2 PoweR Y Fusi. Pumr7 SUP. FUEL lNvENToR. NATHAN C. PRICE Agent Patented Oct. 9, 1951 FUEL CONTROL SYSTEM FOB TURBO POWER PLANTS Nathan C. Price, Los Angeles, Calif., assignor to Lockheed Aircraft Corporation, Burbank, Calif. Application September 8, 1945, Serial No. 615,167, which 433,599, March 6, 17 Claims. This invention relates to internal combustion powerplants and relates more particularly to fuel control systems for internal combustion turbine powerplants. The mechanism or system of the present invention is intended primarily for embodiment in internal combustion turbo powerplants employed to propel aircraft and other high velocity vehicles. This application is a division of my'co-pending application, Serial No. 615,167, filed September 8, 1945, which in turn is a division of my co-pending application Serial No. 433,599, filed March 6, 1942, now Patent No. 2,540,991. It is a general object of the present invention to provide a practical, eillcient and dependable fuel supply and control system for internal com bustion turbine powerplants which system autois a division of application Serial No. 1942, now Patent No. 2,540,991, dated February 6, 1951. Divided and this application April 26, 1947, Serial No. 744,238 (Cl. Gli-35.6) matically establishes and maintains an eflicient air-fuel mixture in the combustion chamber or chambers of the powerplant under all conditions of powerplant operation. Another object of the invention is to provide a y fuel control system of the character referred to in which the pump driving motor is associated with the manually operable throttle control lever, or the equivalent, in such a manner that the fuel pressure supplied to the fuel distributing system is directly related to the fuel quantity requirements at the various powerplant speeds. The power input to the pump driving motor is controlled or adjusted by the throttle control lever so that the speed` of the pump is directly controlled according to the fuel quantity requirements. This results in the conservation of power required for driving the pump and prevents fuel vapor lock due to frictional overheating of the fuel lines, etc. Another object of the invention is to provide a fuel control system embodying a fuel metering means interposed between the fuel pump and the fuel injection nozzles which metering means automatically operates to meter thev fuel in accordance with the air ow through the combustion zone. The metering means' is responsive to the combined function of the rates of flow of air and fuel to the combustion zone and ktends to maintain a proper eflicient fuel-air ratio for each power control setting. A further object of the invention is to provide a fuel control system of the class referred to which incorporates fuel metering means for the primary combustion zone and the secondary or supplemental combustion zone which function in a sequence relation to meter the fuel to both zones. The metering means for the fuel supplied to the supplemental combustion zone is subject to the same regulation as the primary fuel metering device and the aggregate quantity of fuel supplied to the two combustion zones does not exceed the optimum fuel burning capacity of the plant or subject the powerplant elements to excessive temperatures. Other objects and features of the invention will become apparent from the following detailed description of a typical preferred embodiment, throughout which description reference will be made to the accompanying drawings, in which: Figure 1 is a side elevation of a powerplant in which the fuel control system of the invention is embodied, with a major portion broken away plant of the class disclosed in my co-pending applications referred to above. The general st'ucture of the powerplant is briefly described becI use the fuel controlsystem is intimately related with the several powerplant elements and mechanisms. However,.the specific details of the powerplant are omitted as not being essential to an understanding of the invention. The powerplant is adaptedfor use in propelling high speed, high altitude aircraft and is designed to handle a substantial volumetric air flow. The plant comprises generally first and second stage compressors IU and II, a primary combustion chamber I2, a gas turbine I3, and a secondary combustion chamber I4. v The rst stage compressor I0 is of the axial flow type and is equipped at its forward end with a tubular spigot I5 which faces forwardly relative to the direction of flight of the aircraft so as to receive the rammed air. The compressor I0 includes a tubular housing I 6 and a rotor Il supported for rotation in the housing. The rotor impeller blades. The rearor exhaust end of the compressor l0 terminates at a double scroll out-l let housing 20 having a pair of outlet spigots 2l and 22 which communicate with intercoolers 23. The second stage compressorv I lf-isof vthe multistage radralow vand .comprises'three stages 24. 25 and 26 of centrifugal compression arranged in series or tandem relation. The rst stage centrifugal compressor 24 is at the -rear of the scroll housing and has two spigots 21 and 28 receiving the first stage compressed air from the intercoolers 23. The annular exhaust duct of the compressor 24 directs the compressed air through a liquid fed intercooler 30 which, in turn, delivers the air to the inlet 3| of the second stage of centrifugal compression. The second and third stage centrifugal compressors kand 26 'are directly connected in tandem and the air from the final stage compressor passes through diffuser vanes 32 to the combustion chamber I2. The combustion chamber I2' comprises a housing 33 and an annular shroud 34 which together define an annular space leading from the exhaust of the nal stage compressor 26 to the nozzle ring 35 of the gas turbine I3. The housing 33` and shroud 34 are shaped to have an annular series of parallel pockets for containing pa.rs of concentric burner tubes 36. 'Ihe concentric tubes 36 are spaced apart to leave annular combustion spaces which are substantially Venturi shaped to have somewhat confined Zones. Radial openings |49 pass through the walls of the inner tubes 36 at said zones. Fuel injection nozzles 31 extend into the forward ends of the innermost burner tubes 36 and are supplied with compressed air and fuel by annular supply manifolds 38 and 39. The nozzles 31 d.scharge the fuel-air mixture laterally through said openings |48 into the above mentioned annular Venturi shaped passages. Electrical resistance glow plugs 48 extend into the Venturi shaped passages of the combustion chamber I2 to ignite the fuel and air mixture. The gas turbine I3 which is driven by the expanding gases of combustion and air issuing from the combustion chamber I2 includes a housing 4| which extends rearwardly from the combustion chamber. A rotor 42 is xed to a central shaft 43 and rotates within the housing. Impeller buckets or blades 44 on the rotor 42 operate between rows of stator blades 45 on the interior of the housing 4|. The nozzle ring 35 discharges the gases of combustion from the combustion chamber I2 into the expansion zone of the turbine to drive the rotor 42. The secondary combustion chamber I4 is dened by a tubular wall or casing 46 which extends rearwardly from the turbine casing` 4I. The casing 46 is of rearwardly diminishing diameter and its rear end carries a propulsive jet forming nozzle 41. In accordance with the invention supplemental fuel is injected into the secondary combustion chamber I4 when additional power is desired. The means for injecting the supplemental fuel includes a cap 48 on the apex of the turbine rotor and provided with divergent fuel injecting orices 49. The rotor shaft 43 is tubular and conducts the fuel from an elbow fitting 59 to the hollow cap 48. The supplemental fuel injected from the orifices 49 burns in the excess air leaving the turbine I3 to materially increase the thrust output of the powerplant. An internal annular baffle 5I of streamlined cross section is supported in the supplemental combustion chamber to surround and directly oppose the series of fuel injecting orifices 49. The turbine I3 drives the compressors I8 and II through the medium of gear drives or transmissions. A beveled gear 52 is fixed on the forward end of the rotor shaft 43 and meshes with beveiedpinions sa ywhich' are spuneditoradiai. auxiliary shafts 54.-' The compound radial flow l compressor' I l-hasashaft 55 and a beveled gear 56' is fixedv on this shaft to mesh .with the-pinions 53. It will be seemhowv the compressor shaft 55 is driven counter to the turbine rotor 42 by the gearing just described. The compressor shaft 55 in turn drives the rst stage compressor I8 through the medium of a suitable transmission which may include a beveled gear 51 fixed on the forward end of the shaft to mesh with pinions 58. The pinions 58 are fixed on radial shafts 68 which may project from the powerplant housing to drive auxiliaries. The end wall of the first stage rotor I1 carries a beveled gear 6| which is in mesh with the pinions 53 so that the first stage compressor is driven by the gearing. The fuel control system of the invention includes a fuel valve housing 18 containing valves for the primary and secondary fuel injection and cylinder and piston means for operating the same. See Figure 2. A lever 68 is positioned below the valve housing 18 and one end of the lever is pivotally connected with a piston rod 8| projecting from the valve housing 18. A spring 65 is arranged under compression between the other end of the lever 68 and a relatively stationary abutment 66. A coil spring 82 serves as an elastic connection between an intermediate point on the lever 68 and a control lever 83. The spring 65 serves as an elastic fulcrum for the lever 68 and allo-ws the angle of the lever to change without imposing bending forces on the piston rod. The throttle control lever 83 may be located in the flight compartment so as to be conveniently manually operatedv by the pilot or flight engineer. In case the control station for the pilot or flight engineer is remote from the powerplant control auxiliaries, the lever 83 may be actuated through suitable linkages or cables not shown. Ihe throttle control lever 83 is pivotally supported at 84 on a suitable portion of the aircraft structure. i A second coil spring 85 normally acts under compression between a secondary, fuel valve piston rod 86 and a point on the control lever 83 intermediate its fulcrum 84 and the first coil spring 82. The piston rod 86 is parallel `with the above mentioned rod 8| and enters the valve housing 18. The free or outer arm of the throttle lever 83 is adapted to m'ove across a suitably calibrated sector 81. The opposite orfulcrum end of the lever Y83 has `an arm 88 which is adapted to actuate an ignition and fuel pump switch 89 and then actuate a starter switch 9U when the lever is moved across the sector 81 in the direction indicated by the arrow in Figure 2. The above mentioned primary and secondary fuel valve piston rods Bland 86 pass through suitable stuing boxes to enter the valve housing 18, and the two rods lare slidably guided in openings in an intermediate partition or wall 9|. The rods 8| and 86 have gas-tight and liquidtight sliding engagement in the openings. The inner ends of the Arods 8| and 86V have needle points 92 and 93 respectively which are adapted to seat on correspondingly beveled outlet valve seats 94 and 95 when in the closed positions. Outow fuel pipes 96fand 91 extend from the seats 94 and 95 to the `powerplant fuel injection systems. The valve housing 18 has a pair of cylinder bores 98` and 99 and the piston rods 8| and 86 carry pistons `Illl and I9I which have sliding uid tight fits in the bores. The cylinder bores 5 9| and 99 are formed in the lower portion of th valve housing and the respective upper and lower ends of the bores are interconnected by ducts |02 and |03. An yair pressure pipe |04 leads from the discharge of the nal stage compressor 26 to the upper ends of the interconnected cylinder. bores. An inlet nipple |05 may extend through the combustion chamber housing 33 to place the pipe |04 in communication with the high pres-V fsure air duct leading to the combustion chamber. A vacuum pipe |06 leads from the vlower ends of the interconnected cylinder bores 98 and 99 to a Venturi section of a burner tube 36. This starting system may be of the class disclosed and claimed in my co-pending application Serial No.v 615,167,`1ed September 8, 1945. Y In the operation of the apparatus it will rst be assumed that the throttle lever 83 is moved alongthe sector 81 from the stop position to the' position designated ignition. The movement of the lever 83 causes actuation of the switch 89 to complete a low voltage circuit through the glow is shown at s2 in Figure 1. It will be seen that the pipes and connections just described operate to provide differential pressures on the opposite sides of the pistons and |0|. A pair of cylinder bores |01 and |08 is formed in the upper portion of the valve housing 18 above the wall 9|. The above mentioned piston rods 8| and 86 extend through the bores |01 and |08 and carry pistons |09 and ||0 respectively which have loose sliding ts in their respective cylinder bores. A duct in the housing'ls interconnects the lower ends of the cylinder bores I |01 and |08 and a fuel supply pipe ||2 extends from the duct to a fuel feed pump P. The pump `P in turn has its suction or low pressure side in direct communication with the bottom of a fuel storage tank T to avoid the possibility primary combustion chamber and the -pipe 91v carries fuel to the combustion chamber housing i 33 where it passes to the tubular rotorshaft 43 for ultimate discharge from the supplemental fuel orifices 49. The invention includes an actuating and control circuit for the fuel pump P. The pump P is driven by an electric motor M and the invention includes a system for varying the electrical input to the motor in accordance with the throttle setting and the fuel demand of the powerplant. A rheostat |I4 is arranged to be actuated by the piston rod 8| and lever 68. The rheostat ||4 may have a common support with the fuel valve housing and includes a pivoted contact arm ||5. The arm ||5 isactuated by a link ||6 interconnecting the lower end. of the piston rod 8| and a crank secured on the arm H5. Movement of the arm ||5 controls or Varies acircuit completed through the snap switch 89, a battery ill, a conductor ||8,' the 're-v sistance of the rheostat ll4, and a conductor |9 to the motor M. The return of the circuit is by way. of the ground connections illustrated. It will be seen that the electrical power input to the fuel pump drive is adapted to' be varied as a function of the throttle lever setting `and the fuel demands of the power plant. A paral-p lel circuit is completed through the glow plugsV 40 by the switch 89 from the battery |I1 through a conductor and back through thenground connections. The above` mentioned plugs 4'0.'. .At theisame time the circuit to the fuel pump motor'Misjalso closed by the same switch. At vthis ignition position'of the throttle' v lever 83. there is a maximum of rheostat resistance in the motor circuit and, therefore. aminlmum of power input to the fuel pump P. Under' these conditions the pump P produces a comparatively small fuel pressure. When the glow plugs 40 have reached a fuel igniting tempera-v ture, .and the fuel pressure has come up to the starting pressure, thev lever 8,3 lis* advanced to the starte;` position.y This actuates the vswitch 90 to #complete the circuit to the starting system andthepower plant is started. ,When the compressors |9'and and vtliegturloine I3 are up to about 15% of their normal speed, vsufficient air issupiplied by the compressors to establish an appreciable differential pressure in the pipes |04 and -|06. This pressure differential is communicated 'to the fuel valve actuating pistons |00 and |01 in the cylinders 98 and 99, and'tends to move the fuel control needle valves downwardly eff their seats94 and 95. When the throttle controllever 83 is at the starter position on the sector 81, the spring 85 is under suicient vcompression to hold Lthe needle valve 93l ofthe piston rod 86 rmly closed vbut the compression in the `spring 82 is at this pointso balanced that as soon as the ow of airthrough the burner tubes is established to a given value during-the startin'gcycle-ithe above mentioned l resultantwdifferential pressures acting 1 on the piston |00' isy Isufficient*to crack;v or slightly open the needle valve -92 ofstem lill andallowa proper -amountof the'fu'el toifflowthrough line- 96 -v to the primary fueljjet manifold 13s and' thence vto the spray jets 31jin-the burnerftubes This initiates. operation' ofv thepower plant and the f. power plant is brought upv to the idling speed. Upon a further advance of the control leve'r 83 from the starter position the compressive force of the spring 82 is further relaxed, tending to allow` the primary fuelneedle valve 92 to open further and to feed a greater quantity of fuel to the burner jets. However, regulatory forces are immediately and automatically superimposed `upon the fuel control valve motion to meter the fuel allowed to ilow'tothe burner jets in accordance with thequantity of flow of air through the combustion zone." This'insures a proper and em cient fuel mixture toproduce a'nearly constant combustion temperature, thereby protecting the gas turbine from thermal damage. These regulatory forces are applied to the needle valve stems, ForV example, the primary fuel valve stem 8| is urgedinfa direction to re-close the needle valve 92 by thefriction of the increased f ,flow-.offuel'upwardly around the piston |09 and electrical energy |23 which circuit in turnA con-.k- lfrom this disclosure because it is not essential to" an understanding of thepresent invention. The thefforce appliedto the piston |09 through the "pipe |04 tends'to move the needle valve to an open position. The lforceapplied to the piston ma iet-nus opposed totneteppued to the piston |00 and tend'stofreturnitheneedle valve`92 to a closed `position upon theflow of fuel through the ylinders; Thisfrce'is caused byy the difieren-f 1tialpressureimposedLk y y frictional flowof-fue thrQii'ghQthesmall clear'. n the piston |09 by the 7 ance space between the piston and the cylinder wall and toward the valve outlet 94. The flow of fuel from the primary fuel valve is thus a modied combined function of the rates of flow of fuel and air to the combustion zone which tends under all conditions to maintain a proper fuelair ratio for any given power control setting, 'assuming a substantially constant fuel viscosity. Up to this point in the initial stages of Aoperation of the power plant the supplemental fuel needle valve stem 86 has remained in its closed position against the seat 95 under the compressive force of the spring 85. When the control lever is still further advanced on the sector 81 and approaches the position marked Supplemental Fuel, the spring 85 reaches a state of elongation where its compressive force is reduced to a value which permits the supplemental fuel needle metering valve 93 to lift off its seat 95. This allows supplemental fuel to flow through the line 91 and the tubular rotor shaft to the supplemental fuel orifices 49 in the apex 48 of the gas turbine rotor. Supplementary fuel is thus sprayed into the secondary combustion chamber Il Where it burns in the presence of the excess air carried in the gas turbine exhaust. Still further advance of the control lever results in further opening of the supplemental fuel valve 93 to supply an added quantity of fuel to the secondary combustion zone. The metering of the supplementary fuel is subject to the same automatic regulation as that before described in connection with the primary metering valve. As a result the total nal quantity of fuel, both primary and supplementary, does not exceed that required for the burning of all of the air leaving the gas turbine. This avoids the loss of raw fuel through the propulsive nozzle of the powerplant. During the above described forward advancements of the control lever 83 the rheostat III is actuated through its associated linkage to progressively decrease its resistance and thus increase the power input to the motor M which drives the fuel pump P. Accordingly the fuel pressure delivered to the metering valve mechanism varies as an approximate function of the demand. The needle valves of the metering means do not in fact appreciably throttle the fuel but rather the fuel pump speed is directly controlled at the fuel pressure source according to the fuel quantity requirements and the combustion air back pressure. The needles 92 and 93 regulate or trim the now to the exact quantities required with only a small throttling action. This conserves electric power and prevents fuel vapor lock due to frictional overheating. Furthermore, the fuel pressure system makes possible the use of small fuel lines because the fuel pressure drop in the line is compensated for by the fuel control system. Thus a further controlling factor is combined with the automatic characteristics of the fuel metering valve mechanism and tends to impart automatic regulatory characteristics to the unit as a whole. For example, in the event the control lever 83 is moved forward suddenly an immediate increase in fuel pressure with a momentary corresponding increase in ow to the burner results. This momentary increase in flow of the fuel takes care of the acceleration and increased primary and supplementary fuel requirements of the power unit under high power output conditions. Having thus described my invention and the present preferred embodiments thereof, I desire to emphasize the fact that many modicaticns 8 may be resorted to in a manner limited only by a just interpretation of the following claims. Iclaim: 1. A power plant comprising a compressor, a gas turbine driving the compressor, a primary combustion chamber between the turbine and compressor, a secondary combustion chamber at the downstream side of the turbine, fuel injection means for the primary combustion chamber. fuel injection means for the secondary combustion chamber, a source of fuel under pressure, means responsive to pressure conditions in the compressor and primary combustion chamber for metering the delivery of fuel from said source to the primary combustion chamber, means responsive to pressure conditions in the compressor and primary combustion chamber for metering the delivery of fuel from said source to the secondary combustion chamber, and a control operable to sequentially operate said metering means so that a given fuel-air ratio is first established in the primary combustion chamber and subsequently a given fuel-air ratio is established in the secondary combustion chamber. 2. A power plant comprising a compressor, a gas turbine driving the compressor, a primary combustion chamber between the turbine and compressor, a secondary combustion chamber at the downstream side of the turbine, fuel injection means for the primary combustion chamber, fuel injection means for the secondary combustion chamber, a source of fuel under pressure, means sensitive to fuel ow to the primary chamber and to air pressure conditions in the compressor and primary combustion chamber for metering the delivery of fuel from said source to the injection means of the primary chamber, means sensitive to fuel flow to the secondary chamber and to air pressure conditions in the compressor and primary combustion chamber for metering the delivery of fuel from said source to the injection means of the secondary chamber, and a single manual control for sequentially conditioning said metering means for operation. 3. A gas turbine power plant comprising a compressor, a turbine, a combustion chamber between the compressor and turbine, a source of fuel, a pump for pumping fuel under pressure from said source to the combustion chamber for injection therein, variable speed power means for operating the pump, metering means between the pump and combustion chamber sensitive to fuel flow pressure and to the rate of air flow from the compressor and operable to effect a fine regulation of fuel flow to the combustion chamber, and means for varying the speed of operation of the power means to effect the primary regulation of fuel delivery to the combustion chamber. 4. A gas turbine power plant comprising a compressor, a turbine, a combustion chamber between the compressor and turbine, a source of fuel, a variable output pump means for pumping the fuel to the combustion chamber, means interposed between the pump means and combustion chamber sensitive to fuel flow pressure and to the rate of air flow into the combustion chamber to effect a fine regulation of the fuel now to the combustion chamber, and manually operablemeans for varying the speed of operation of the pump means to eifect a primary regulation of fuel delivery to the combustion chamber. 5. A gas turbine power plant comprising a compressor, a turbine, a combustion chamber between the compressor and turbine. a source of fuel, a variablefoutput pump for pumping the' speed of operation of the pump to effect the primary regulation of fuel delivery to the combus tion chamber, and manually operable means for actuating the primary' control means and for biasing said fine regulation means. 6. A gas turbine power plant comprising a ccmpressor, a turbine, a combustion chamber between the compressor and turbine, a source of fuel, a variable output pump for pumping the fuel to the combustion chamber, means interposed be` tween the pump and combustion chamber sensitiveto fuel flow pressure and to the rate of air flow into the combustion chamber to effect a fine regulation of the fuel flow to the combustion chamber, a primary control means for varying the speed of operation of the pump 'to effect the primary regulation of fuel delivery to the combustion chamber, and a single manual control for simultaneously operating the primary control means and biasing said ne regulation means. 7. A gas turbine power p'ant comprising a compressor, a gas turbine, a combustion chamber between the compressor and turbine, a pump for pumping fuel into the combustion chamber, vari- .abe power means for operating the pump, fuel metering means interposed between the pump and the combustion chamber including a fuel metering valve, a piston associated with the valve and acted upon by the fuel flowing to the combustion chamber to urge the valve closed, and a manually operable throttle control for simultaneously varying the output of said power means and the position of the valve. 8. A gas turbine power plant comprising a compressor, a gas turbine, a combustion chamber between the compressor and turbine, a pump for pumping fuel into the combustion chamber, variable power means for operating the pump, fuel metering means interposed between the pump and the combustion chamber including a fuel metering valve, a piston associated with the valve, means for applying pressure from the compressor to one side of the piston, means for supplying pressure from the combustion chamber to the other side of the piston, the dierential in said pressures tending to operate the metering valve, and a manually operable control for varying the output of said power means and the position of the valve. , ond piston associated with said valve, means for supplying pressure from the compressor to one side of the second piston, means for supplying pressure from the combustion chamber to the other side of the second piston, the differential in said pressures tending to operate the metering valve, and a manually operab'e throttle control for simultaneously varying the output of said power means and the position of the valve, 10. A gas turbine power plant comprising a compressor, a gas turbine, a primary combustion chamber between the compressor and turbine, a secondary combustion chamber, a pump for pumping fuel to said chambers, variable power means for driving the pump, a fuel metering means interposed between the pump and each of said chambers, each metering means including a fuel metering valve, and a piston associated with the valve acted upon by the fuel fiowing to the respective chamber to urge the valve closed, and manual means for sequentially operating said valves and for varying the output of said power means. g 11. A gas turbine power plant comprising a compressor, a gas turbine, a primary combustion chamber between the compressor and turbine, a secondary combustion chamber, a pump for pumping fuel to said chambers, variabe power means for driving thc pump, a fuel metering means interposed between the pump and each of said chambers. each metering mans includingr a fuel rretering valve, a first piston associated with the valve and acted upon by the fuel flowing to the respective combustion chamber to urge the valve closed, a second piston associated with the valve, means for supplying pressure from they v compressor t0 one side of the second piston, and means for supplying pressure from the combustion chamber to the other side of the second piston, the differential in said pressures tending to operate the valve, and manua'ly operable means lfor simultaneously varying the output of said and the primary chamber, a second fuel metering valve means interposed between the pump and the supplemental chamber means for dividing tbe fuel flow from the pump into separate streams for flow through said separate valve means, a single manual control lever. and operative connections between the lever and said metering valve means related so that the metering valve means are operated in sequence upon movement of the lever. 13. A gas turbine power plant comprising a compressor, a gas tvrbine, a primary combustion chamber between the compressor and turbine, a supplemental combustion chamber at the downstream side of the turbine, a pump for pumping fuel to said chambers, a first fuel metering means interposed between the pump and the primary chamber, a second fuel metering means interposed between the pump and the supplemental chamber, a manual control lever, and elastic means connected between the lei-er and said metering means related so that the metering means are operated in sequence upon movement of the lever. 14. A gas turbine power plant comprising a compressor, a gas turbine, a primary combustion chamber between the compressor and turbine, a supplemental combustion chamber at the downstreamside of the turbine, a pump for pumping fuel to said chambers, a first fuel metering means interposed between the pump and the primary chamber, a second fuel metering means interposed between the pump and the supplemental 11 chamber, a manual control lever, and compression springs engaged between the lever and said metering means related so that the metering means are operated in sequence upon movement of the lever. l 15. A gas turbine power plant comprising a compressor, a gas turbine, a primary combustion chamber between the compressor and turbine, af supplemental combustion chamber at the downstream side of the turbine, a pump for pumping fuel to said chambers, a first fuel metering means interposed between the pump and the primary chamber, a second fuel metering means interposed between the pump and the supplemental chamber, a manual control lever, elastic operative connections between the lever and said metering means operable to produce sequential operation of the metering means upon movement of the lever, and a calibrated sector associated with the lever for indicating the operative condition of the two metering means. 16. In a gas reaction propulsive unit, apparatus comprising in combination, a flow system for air and gases including a gas turbine, a nozzle communicating with the exhaust of said turbine and adapted to produce a propulsive jet, primary and secondary combustion chambers, the ` primary combustion chamber including an air and fuel mixing region having a high velocity throat, `means to introduce combustion gases from said primary combustion chamber into said turbine, means to pass combustion gases from said turbine into said secondary combustion chamber and the said nozzle, a compressor driven by said turbine, and means to pass compressed air from said compressor to said primary combustion chamber; means to introduce fuel to said primary combustion chamber; means to introduce fuel into said secondary combustion chamber; a manually settable fuel throttle control; and means responsive to the combined functions of the rate of now o! compressed air into said primary combustion chamber measured by the differential between the pressure in said compressor and the pressure in said throat of the primary combustion chamber and the throttle control setting to meter the rate of said introduction of said fuel into the primary and secondary combustion chambers. 17. Apparatus according to claim 16 in which said means to meter fuel includes a primary metering valve for metering fuel for the primary combustion chamber .and a secondary metering valve for metering fuel for the secondary combustion chamber operable successively first to control the introduction of fuel into the primary combustion chamber only, and subsequently to control introduction of fuel into both the primary and secondary combustion chambers. NATHAN C. PRICE. REFERENCES CITED The following references are of record in the file of this patent: UNITED STATES PATENTS and 242.