US758400A - Governing mechanism for turbines. - Google Patents

Description

No. 758,400. PATENTED APR. 26, 1904.

' J. WILKINSON.

GOVERNING MECHANISM FOR TURBINES.

- APPLICATION FILED FEB. 23, 1904.

NO MODEL. 1 2 BKEETfl-SHEET 1.

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I PATENTED APR. 26, 1904.

S E N I B R T R 0. W M R I N m WC .E M G N I N R B V 0 G APPLICATION FILED FEB. 23 1904.

llll 20697666 as am @a 6 a w w a 0, WASHINGTON n c Noi 758,400.

UNITED STATES Patented April 26, 1904.

PATENT OFFICE.

JAMES WILKINSON, OF BIRMINGHAM, ALABAMA, ASSIGNOR TO THE WILKINSON STEAM TURBINE COMPANY, OF BIRMINGHAM, ALA- BAMA, A CORPORATION OF ALABAMA. r

GOVERNING MECHANISM FOR TURBINES. k

EEEGIFICATION forming part of Letters Patent No. 758,400, dated April 26, 1904:.

Application filed February 23, 1904. Serial No. 194,853. N0 model.) 7

To all whom, it 77000; concern.-

Be it known that I, J AMES WILKINSON, a citizen of the United States, residing at Birmingham, in the county of J etferson and State of Alabama, have invented certain new and useful Improvements in Governing Mechanism for Turbines, of which the following is a specification.

My invention relates to improvements in fluid-pressure governing mechanismfor turloines, and is particularly designed with a view to perfecting a simultaneous control of rows of valves across the stages of a turbine operating by stage expansion of the fluid-pressure.

It is an object of my present invention to adapt the fluid-impact governor, which forms the subject-matter of a separate application, to control the supply-valves separately by means of independentfluid-passages formed in a simple and economical manner and subjected to the injector or ejector action ofa fluidjet under the control of a pivotally-swinging controller-nozzle. 7

My invention furthercomprises improvements in the operation of stage-valves under the control of the supply-valves and the de- 'sectional view also broken away and taken on a curved vertical plan through the center of a row of working passages disposed around the turbine and illustrating the governing mechanism. Fig. 8 is an enlarged detailed plan view of the controller mechanism with the nozzle-casing removed. Fig. 4 is an enlarged vertical sectional View on the line a m, Fig. 3. Fig. 5 is abottom view of the discharge end of the controller-nozzle shown enlarged. Fig. 6 is a detailed perspective view of one of the grooved strips forming conduits for the valveactuating fluid.

The same reference characters refer to the same parts throughout the drawings.

I have illustrated my invention as applied to a two-stage turbine having a supply-head 1,

adiaphragm-partition 2, and ashell 3, forming an exhaust-chamber, which interlock and are surrounded by a strengthening-shell A. This shell has a shoulder 5 atits exhaust end which engages-a corresponding shoulder 6 around thershell 3 and is also providedat its supply end with an annular channel 7, within which a sectional locking-strip 8 is securely bolted by tap-screws 9. The eifect of the shoulder 6 and the looking-strip 8 is to form stops between which the supply and exhaust end sections and the diaphragm-partitions are held firmly in position against internal pressure.

The compartments into which the interior I of the turbine is divided by thediaphragm 2 form stages or wheel-compartments within each of which rotates a wheel 10, provided with a peripheral row of buckets 11. Motor fluid is delivered from any suitable source to an annular supply-passage 12 in the head, Which communicates by branch passages 13 with valve-chambers l4, bored into the head from its under side and disposed near its pe riphery. Plugs 15, provided with a curved passage-way 17, are screwed into the lower or open ends of the chambers 14 and serve to close the same except for the opening formed by the passage 17. The plugs are disposed so that these passages 17 are in alinement with short passages 18, bored at an angle through the head and serving as delivery'ends for the nozzle-passages, which discharge the fluid-pressure admitted-through passages 13 v at an angle against therevolving buckets 11. By this construction the plugs 15 serve the double purpose of closing the valve-chamber and forming'the intermediate curved part of the supply-nozzles, which effects a marked economy in manufacture. The supply-valves are eachconnected by a stem 20 to a piston the annular channel 22 to the passage 23 for" Too the purposes hereinafter described. A small cylinder 27 leads from the top of chamber 14 and opens through a port 28 into a channel 29. This channel is formed in the upper surface of the head 1 and continues around theturbine, being adapted to receive superimpo'sed strips 30, which fit pressure-tight within the channel and are provided with grooves 31 on their under sides, as shown more clearly in Fig. 6. By reference to Fig. 2 it will be seen that this channel 29 will vary in depth at different points. This construction is necessary in view of the fact that the several grooved strips are of varying length, each being adapted to successively conduct fluidpressure to a port 28, beyond which point the groove 31 terminates and forms a closed end for the passage. The channel 29 has its greatest depth at the end nearest the fluid-pressure-governing mechanism, hereinafter described, and is decreased in depth by the formation of shoulders whose height corresponds with the thickness of the strips 30. Thus the end of the bottom strip 30, leading to the first valve cylinder, will abut against the shoulder 32, whose top surface is of an even height with said strip and serves as a support for the strip 30, which rests upon the bottom strip and forms the conduit for the valve-actuating fluid conducted to the second valve-cylinder of the series. A second shoulder 33 will support "the strip above the one last mentioned, and as many other shoulders will be provided as there are strips 30. It will thus be evident that the depth of the channel at its end farthest from the governing mechanism will correspond with the thickness of the top strip 30, which strip will be even with the top of head 1 and held firmly in place by the flanged extension 34 of the locking-strip 8, which is securely bolted to the head by tap-screws 35. Since the several strips are superimposed, it follows that this flange 34 will hold them all firmly and securely in position, and, if desired, packing may be used to prevent the leakage of pressure between the passages.

In adapting the fluid-pressure impact-controller mechanism, more fully described and claimed in a pending application, to control the potential of the pressure in the several conduits 31 I provide a circular block 36, seated in a recess in the head and provided with a transverse passage-way 37 and a cut-away portion on the side, which forms a continuation of the channel 29. As will be seen in Fig. 4, this cut-away portion leaves a thin division wall or tongue 38, forming a side of the passage 37 and is curved at 39. The several strips 30 are also curved to correspond with the cut-away portion of block 36 and continue upwardly toa point slightly above the top surface of the flange 34, which also serves the purpose of holding the block 36 in position. This thin division-wall 38 also continues to the top of flange 34, and it will be noted that the upper ends of the strips 30 increase slightly in height, so that their upper ends conform to an arc corresponding with the swing of the pivoted controller-nozzle 40, which is mounted in the casing 41, communicating at its upper end with any suitable source of pressure and secured at its lower end to flange 34. The

controller-nozzle 40 comprises a cylindrical body portion mounted to rotate in a seat 42, formed in said casing and having a transverse port therethrough, which flares at its inlet end and at its discharge end communicates with a nozzle 43, which is provided with screwthreads to engage a correspondiugly-threaded recess in said cylindrical body portion. The casing 41 is provided at its discharge end with a compartment 44, within which the nozzle 43 swings and which is reduced in size at its lower end to conform in shape with the area occupied by the passage 37 and the group of strips 30. At its upper end the chamber is enough larger than the nozzle to leave ample clearance for the escape of the controller-pressure around it to passage 37, as will be seen in dotted lines, Fig. 1. By reference to Fig. 5 it will be noted that the side of the nozzle toward the strips is flattened, while its other side, which is normally exposed above the passage 37, is rounded. The division-wall 38 and the strips 30 are very much reduced in thickness at their upper ends, so that they form as thin division-walls as possible to reduce the friction of the fluid-jet and the throw necessary for the nozzle to control the discharge of pressure into all of them.

To enable the locking-ring 8 to be moved inwardly out of engagement with the channel 7, so that the shell 4 may be dropped and access gained to the interior of the turbine, I provide the flanged portion.34 with a removable section or block 45, which covers or includes one-half of the opening through which the division-plate 38 and strips 30 project. The opening in portion 34 is wide enough to enable its shoulder to clear channel 7 when block 45 is removed, and as the section of the locking-strip opposite the governor device is movedinwardly toward the shaft this shoulder 8 will clear the channel, and the locking-strip may then be removed without disturbing the strips 30. Any suitable governor mechanism may be used to move the crank 46, which operates the shaft 47, connected to the nozzle 40 and leading'through a suitable packing-gland 48.

Itbeing noted that the passage 37 in block 36 is in alinement with a nozzle-passage 49, leading through the head and discharging against the buckets 11 when the nozzle is moved opposite passage 37, the fluid-jet will pass directly thereinto and will act with an ejector'efi'ect to create a partial vacuum in the controller-chamber 44 and in the valve-controlling conduits formed by the strips 30 and opening into said controller-chamber. As the act to raise the pressure in them to a point.

nearly equal to its own pressure, and at the same time the fluid will escape around I the nozzle and passing through the chamber 44- will enter passage 37 and nozzle 49 and do useful Work in driving the turbine. As the nozzle moves over the passages, it is my purpose to construct the latter so that the fluidjet will successively act with its full injector or ejector action according to its direction of movement upon each of the passages. I thus avoid the creation of any intermediate pressures in any of the valve-controlling passages and move the valves always to an open or closed position.

Having thus described my governor mechanism for admitting the fluid-controller pressure to the several valve-cylinders, I will now describe the action of the supply-valves.

The upper end of each passage 23, leading through the supply-valves, constitutes a valveseat which is normally closed when in its lowered position by a secondary valve 50. This secondary valve 50 has an enlarged piston-head which moves pressure-tight within the cylinder 27 and is beveled at its upper end to seat against the beveledupper end of cylinder 27. Referring to 'Fig. 2, it will be noted in connection with the second valve 19 of the series, which is shown open, that this secondaryvalve 50 is lifted a sufiicient distance from its seat to permit the escape of pressure from above piston 21 through passage 23 into the nozzle-passage 17, leading to the first stage. Pressure is admitted above this piston by a passage 51,

leading therethrough and smaller in size than passage 23. When it is desired to cut oif all fluid-supply from the turbine, the controllernozzle is moved to a position directly over all of the fluid-passages 31, so that the pressure therein will be raised to a point suflicient to move the secondary valves 50 to a seated position, thus closing passages 23 and permitting pressure above and below piston 21 to be equalized through passage 51. Under these conditions the valve will be slightly unbalanced and will have a tendency to move upwardly toward its open position; but this is overcome by the combined action of the controller-pressure against the piston-head of the auxiliary Valve 50 and the suction action of the fluid-stream through the nozzle 17 against valve 19. This suction and the action of the controller-pressure will cooperate to moveall of the valves to their closed position, and the stream of controller fluid passing through nozzle 49 will act to drive the turbine under its friction load. As the load increases the controller-nozzle 43 will be moved to successively create by its ejector action a partial vacuum in the outer passages 31 of the series, thus cutting off controllerpressure from above the valves to be openedand causing the pressure above p1stons 2l to act against the shouldered heads of the secondary valves 50 and raise them from their seats. By thus opening communication through passage 23, between the upper end of cylinder 14 and the first stage, the high pressure above piston 21 will flow through passage 23 and be reduced, since this passage is much larger than passage 51, and will therefore discharge pressure faster than it can be supplied by the latter passage. The high pressure below piston 21 will accordingly raise it and open the provide passages 52, leading from the upper 5 valve 19. A s this valve leaves its seat the ejector 1 ends of the cylinders 14 at a point opposite the circular passage 22 in piston 21 when the latter is in its raised position. This passage 52 connects with a passage 53, formed bya recess in the casing, and a grooved block 54, inserted and secured therein and from which a branch passage 55 leads through the casing and a block 56 and enters the upper end of a chamber 57, bored into the diaphragm 2. This chamber, which is closed at its upper end by a block or plug 56, serves as a cylinder for a piston 58, which moves pressure-tightthere in and is provided with a depending stem 59, leading through a stuffing-box 60 and engaging a lever 61, which operates a crank 62, connected to a rotary stage-valve. seated in the nozzle-passage 63, which leads through the diaphragm 2 and delivers motor fluid against the rotating buckets 11 in the second wheel compartment. I admit pressure below piston 58 through a passage 64, formed between the shell 4 and the casing of the turbine, preferably by a recess formed in said shell. through a passage 66 and withdrawn through Pressure is admitted to thisjacket Thisvalve is a similar passage (not shown) on the opposite side of the turbine. In operation when the supply-valve has moved to its closed position passage=53 will be exposed to the boiler-pressure which exists above piston 21 by reason of passage 51, and this pressure is admitted above a stage-piston 58 through passages 53 and 55 and will move the piston downwardly and close the stage-valve. It will be noted that the piston 58 is unbalanced by reason of this stem 59, so that boiler-pressure may exist on both sides of it, and in this case it will always move to its closed position. When the supply-valve rises to its open position, passage 52 will communicate with the annular passage 22 around stem 21. This passage in turn communicates by a passage 26 with the suction-passage 23 through the valve, so that the valve-actuating fluid is discharged into a supply-nozzle and acts with full efliciency throughout all the stages. Not only will the high pressure in cylinder 57 and the passages leading thereto be discharged through passages 26 and 23, but the suction action of the fluid in nozzle 17 will maintain the pressure in cylinder 57 so low that the pressure below piston 58 moves it to its upper position and opens the valve. The passage 53 preferably connects a supply and one or more stage valves in the line of the fluids flow, in which case it will be noted in Fig. 2 that the stage-valve lettered A will be in the line of the fluids flow from nozzle 49 and may be controlled by a branch passage leading from one of the passages 53 on either side of it, and the stagevalve lettered B will be controlled by the first supply-valve of the series.

The pistons for the stage and supply valves and their seats are beveled to cause them to act without intermediate operating positions. Each supply-valve may control any desired number of stage-valves, and passages 53 may connect the supply and stage cylinders in any manner as occasion may require.

By utilizing the steam-jacket pressure to open the stage-valves the construction of my governing mechanism will be very much simplified and a number of unnecessary fluid-passages dispensed with.

I have shown the annular radiating fins 67 opposite the bucket-wheel as formed integral, with an annular ring 68, which is inserted between the head and diaphragm and cut away for the groove-strip 55 and passage 53.

Though I have shown and described a restricted passage 51 to admit the motor fluid above piston 21, it will be obvious that the piston may be adapted to permit a leakage around it equivalent to the volume of pressure admitted through passage 51, which may then be dispensed with. The construction and arrangement of parts may be further changed without departing from the spirit of my invention.

Having thus described my invention, what I claim as new, and desire to secure by Letters Patent, is- 4 1. In a turbine, a supply-head, a valve-cylinder therein, a piston-valve in said cylinder and a plug closing the lower end of said cylinder and having a passage therethrough serving as a supply-nozzle for the motor fluid.

2. In aturbine, a wheel-compartment, asupply-head therefor, a cylinder therein, a plug serving as a head for the lower end of said cylinder, a nozzle-passage for the motor fluid leading from said cylinder through said plug, and a piston-valve in said cylinder to control said motor fluid.

3. In a turbine, a stationary element, a cylinder therein, a passage admitting motor fluid thereto, a valve in said cylinder controlling the admission of motor fluid to a nozzle-passage, and a plug serving as a seat for said valve and comprising the intermediate portion in said'nozzle-passage.

p 4:. In a turbine, a fluid-induction nozzle formed in a stationary element, a valve therefor, and a detachable element forming a seat for said valve and the admission and curved portion of said nozzle.

5. In a turbine, a fluid-induction nozzle formed in a stationary element, a piston-valve therefor, a cylinder for said valve, and a detachable elementforming a lower head for said cylinder and the admission and curved portion of said induction-nozzle.

6. In a turbine, a fluid-induction nozzle leading through a stationary element constituting a supply-head for a wheel-compartment, a cylinder bored from below into said element, means to supply motor fluid to said cylinder, a valve therein, and a plug inserted into the lower end of said cylinder and provided with a curved passage therethrough and a seat for said valve at the inlet end of said passage, and a passage, forming the delivery end of said nozzle, which leads through said element and with which the passage in said plug is normally in alinement.

7. In a multiple-stage turbine, supply and stage valves controlling the flow of motor fluid through the turbine, means to operate said supply-valve, fluid-pressure means under the control of said supply-valve to move said stage valve in one direction, and a steamjacket pressure to move said valve in the opposite direction.

8. In a multiple-stage turbine, supply and stage valves, and fluid-pressure means to operate said stage-valves comprising a fluidpressure under the control of said supplyvalves, and an opposing pressure derived from a fluid-chamber utilized to superheat the turbine.

9. In a multiple-stage turbine, supply and stage valves, a movable piston to operate said stage-valve, means to admit fluid-pressure under the control of a supply-valve to move said piston in one direction, a steam-jacket, and means to admit the pressure from said jacket to oppose said first-mentioned pressure.

10. In a multiple-stage turbine, series of supply and stage valves, a governing means for said supply-valves, fluid-pressure means controlled by said supply-valves to operate said stage-valves, a compartment supplied with fluid-pressure, and a series of passages lead ing therefrom to admit pressure to operate said stage-valves when said first-mentioned operating pressure is reduced or cut off. a

11. In a turbine wherein the motor fluid is fractionally expanded, a plurality of wheelcompartments, one or more nozzles between compartments, a valve or valves for said nozzles, a constant pressure from a compartment independent of said wheel compartments .which tends tomove said valve or valves to an open or closed pos1t1on, and means, under the control of a governing mechanism, to regulate a fluid-pressure adapted to move said valve or valves in opposition to said constant compartment-pressure.

12. In a multiple-stage turbine, wheel-compartments, stage-valves, fluid-pressure motors to operate said valves, a compartment, independent of said wheel-compartments, which supplies one of the operating pressures to said motors, and means, under the control of supply-valvesflco cut on or ofi the other operating pressure to said motors.

13. In a turbine operating by stage expansion, wheel compartments, nozzle-passages and valves therefor admitting the motor fluid to the several compartments, governor-controlled piston-valves supplying motor fluid to the turbine, piston-actuated valves between compartments, cylinders for said pistons, a steam-jacket surrounding a wheel-compart ment, means to admit the jacket-pressure to one end of said cylinders and a passage, leading from the other endof each cylinder to a supply-valve cylinder, in which a high or-low pressure is maintained according to the position of said supply-valve.

1 1. In a turbine, a motor-fluid-supply valve, a cylinder within which said valve moves pressure-tight, a passage leading longitudinally through said valve, a secondary governor-controlled valve to close said passage, and means to admit the motor fluid to both ends of said cylinder.

15; In a turbine, a piston-actuated valve reciprocating in a cylinder and controlling the admission of motor fluid to a nozzle-passage, a passage leading from below the valve to the upper end of said cylinder, a smaller passage admitting the motor-fluid pressure above said piston-valve, and a secondary valve to control the movement of said piston-valve by opening or closing said first passage.

16. In a turbine, a piston-actuated valve, a nozzle to which pressure is admitted under the control of said valve, and means to utilize the suction action of the fluid stream in said nozzle to-assist in opening said valve. V

17. In a turbine, a piston-actuated valve, a

nozzle to which pressure is admitted under thecontrol of said valve, and means to utilize the suction action of the fluid stream in said nozzle to move said valve to its closed position.

18. In a turbine, a nozzle-passage, a pistonactuated valve controlling the flow of motor 1 fluid therethrough, and means to utilize the ejector or suction action of the fluid stream to assist in opening and closing said valve.

19. In a turbine, a supply-head fora wheelcompartment, a chamber forming a cylinder therein, a piston-valve movable within said cylinder, a nozzle-passageopened or closed by said valve, an extension depending from said valve and disposed Within said nozzle-passage, a passage leading through said piston and extension, a governor controlled secondary valve to open orclose said latter passage, and

means to admit motor-fluid pressure above said piston-valve.

20. In a turbine, a stationary elementQa fluid-supply valve, a secondary valve controlling fluid-pressure means to operate said supply-valve and seated thereon and movable therewith.

23. In a turbine, a reciprocating motorfluid-supply valve, fluid-pressure means to actuate said valve and'a secondary valve, which controls said fluid-pressure means to open or' close said supply-valve, and seats upon said supply-valve in one of its operating positions. 7 24. In a turbine, a nozzle-passage, a recip- 1 rocating valve therefor, and a secondary valve seated upon and movable with said supply valve toward its closed position, and independent thereof as it moves to its open position, said secondary valve controlling pressure means to operate said supply-valve.

25. In a turbine, the combination with amotor-fluid valve, a casing provided with two connecting chambers in one of which a piston for operating said valve moves, a permanently open restricted passage by which the same pressure is caused to exist on each side of said piston, a passage forming an-exhaustingconduit and open to the pressures existing above and below said piston-valve, and a secondary Valve in the other of said chambers which moves under the control of a governing mechanism to open and close said exhausting-conduit. r

26. In a turbine, the combination with a main valve operated by a piston, of a casing having two connecting-chambers, one of which constitutes a cylinder for said piston, means to admit the pressure below said piston to the cylinder above it, a secondary piston-actuated valve movable in said other chamber, and a passage, leading through said main piston and valve, which is closed by said secondary valve to cause said main valve to move toward and assume a closed position and is opened by said secondary valve to cause the main valve to move toward and assume an open position.

27. In a turbine, the combination with a main valve operated by a piston, of a cylinder therefor exposed to a high pressure below said piston, means to provide for a limited flow of said high pressure to the cylinder above said piston and a passage adapted to discharge said pressure above said piston at a point below said main valve when the latter is open, and means to close said latter passage when said main valve is closed.

28. In a turbine, a valve operated by a piston, a casing having a cylinder for said piston which is exposed at one end to the motor-fluid pressure, means to effect a restricted circulation of motor fluid whereby it passes from below said piston to the chamber above it and thence to a point below said valve, and means to interrupt the flow of said pressure from the chamber above said piston when it is desired to close the valve.

29. In a turbine, a main valve operated by a piston, a cylinder therefor, a port admitting motor-fluid pressure below said piston and a restricted passage admitting it above said piston, a passage leading through said piston and valve and subjected at its lower end to the suction action of the motor-fluid stream when said valve is open, and a secondary valve to close said suction-passage and assist the pressure admitted above said piston in moving the latter toward its valve-closed position.

30. In a turbine, a main and a secondary valve both of which are operated by pistons, a casing having two chambers therein serving as cylinders for said pistons, the cylinder for said secondary valve opening into said mainvalve chamber, a restricted passage through which the motor-fluid pressure existing below said main-valve piston is admitted above it, a passage leading through said main valve and piston by which the pressure above said piston is wholly or partially exhausted and which is opened and closed by said secondary valve, and means to admit a controller-pressure to one end of said secondary-valve cylinder while the other end is open to the pressure existing above the main-valve piston.

31. In a governing mechanism for motors, a controller-chamber through which a continuously-flowing stream of fluid passes and enters a normally open passage, a plurality of controller-fluid conduits for a plurality of motor-fluid valves, and means to change the course of said stream to control the operation of said valves.

.32. In a fluid-pressure-governing mechanism for motor-fluid Valves for turbines, a pivoted movable controller-nozzle, and a stream of fluid-pressure which acts under the direc- 5 tion of said nozzle to control the operation of said valves.

33. In a motor, aplurality of fluid-pressureactuated valves for the motor fluid, a plurality of conduits for the valve-actuating fluid, and means utilizing the impact eflect of a continuously-flowing stream of fluid to severally control the operation of said valves.

34. In amotor, a plurality of fluid-pressurecontrolled valves for the motor fluid, a plurality of conduits for the controller fluid, and fluid-impact means under the control of a governor-nozzle to successively raise the pressure in said conduits and control the operation of said valves.

35. In a motor, a plurality of motor-fluid nozzles, fluid-actuated valves therefor, a plurality of separate passages for valve-controlling fluid, means, responsive to the pressure in said passages, which control the operation of said valves, and a governor-nozzle controlling the operation of said means.

36. In a motor, a plurality of motor-fluid nozzles, fluid-actuated valves therefor, a plurality of separate passages for valve-controlling fluid-pressure, secondary valves, actuated by said controlling fluid, which control the operation of said first-mentioned valves, and a governor-nozzle utilizing a stream of fluidpressure to control the operation of said secondary valves.

37 In a motor, a fluid-induction nozzle, a main valve, a secondary piston-valve controlling fluid-pressure operating means for said main valve, a fluid-conduit one end of which is closed by said piston-valve and means, utilizing a continuously-flowing stream, to vary the pressure in said conduit.

38. In a motor, a plurality of fluid-induction nozzles, a plurality of main valves for said nozzles. secondary pistonvalves controlling fluid-pressure means to operate said main valves, a plurality of fluid-conduits which terminate in cylinders for said piston-valves, and a governor-nozzle to control, by fluid-pressure means, the operation of said secondary IIO grooved strips disposed therein and forming conduits which lead from a source of controller-pressure to a plurality of valves.

42. In a turbine, a supply-head, a plurality of longitudinally-grooved strips of varying length secured thereto and forming conduits which lead successively to the several motorfluid-supply valves.

43. In a turbine, a supply-head, a plurality of longitudinally-grooved strips of varying length, a shouldered channel in said head in which said strips are secured, and a plurality of passages each of which communicates with a channel and with a valve-cylinder.

44:. In a turbine, a supply-head, a channel therein, a plurality of contiguous strips forming conduits disposed in said channel, and

' means to secure said strips in position com- 46. In a turbine, afluid-pressure-controller chamber, a plurality of adjacent passages leading therefrom, one of which is normally open,

and the others of which are normally closed at their outer ends and formed by channelways between contiguous strips whose ends enter said chamber, and a movable controllernozzle which directs a flowing stream of fluid into part of said passages, which stream, in passing out through said normally open passage, acts with an ejector effect to exhaust the pressure from so many of said closed passages as are not exposed to the direct action of said stream.

4:7. In aturbine, an induction-passage, a motor-fluid-supply valve operated by a piston, a chamber for said piston, a pressure-controlling passage leading through said piston and opening into said induction-passage below said valve, and a secondary valve to open and close said pressure-controlling passage.

48. In aturbine, amotor-fluid valve, achamher therefor, a passage leading through said valve, means to permit a restricted flow of pressure into the chamber above said valve, and a secondary valve to open and close said passage through the main valve.

4E9. In a motor, a plurality of contiguous strips between which conduits are formed, a plurality of valves whose operation is controlled by the fluid-pressure in said conduits, 'and means to control the admission of fluidpressure to said conduits.

In testimony whereof I have signed my name H. M. HARTON, EVANS JOHNSTON.

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