US3084906A - Governor control - Google Patents

Description

April 9, 1963 B. E. WHEELER GOVERNOR CONTROL 2 Sheets-Sheet 1 Filed Aug. 26. 1960 FIG /A mVENro'R rPo/v f. wia .FP

April 9, 1963 E. E. WHEELER GOVERNOR CONTROL 2 Sheets-Sheet 2 Filed Aug. 26,' 1960 -------ilif -IIIIIIAIII'IIII-l 1N VEN TOR Y VPO/vf. ryA/fai? 3,084,906 GOVERNR CONTROL Byron E. Wheeler, 1254 Cabrillo Ave., Burlingame, Calif. Filed Aug. 26, 1960, Ser. No. 52,690 7 Claims. (Ci. 253-24) The invention relates to devices especially concerned with speed and other related controls of relatively large hydraulic propulsion machinery of the sort utilizing an impeller acted upon by impinging water. One sort of device of this nature is an impulse water wheel usually connected by a common shaft to an electric generator and acted upon by one or more jets of impelling water emerging from nozzles controlled by axially movable needles. A device of this general nature is shown in Patent 2,707,938 issued May l0, 1955, and in Patent 2,857,885 issued October 28, 1958. A quite similar device is shown in the copending application of Percy B. Dawson, Jr., and Byron E. Wheeler, the applicant herein. That application is entitled Governor Controller and bears Serial No. 832,312 and was tiled August 7, 1959.

An object ofthe present invention is to provide a mechanism which is particularly effective to maintain the desired sort of speed control on a hydraulically driven unit despite variations in load on the unit and despite certain other variations in operating circumstances.

It is a particular obiect of the invention to provide a governor control useful in connection with a water wheel having a plurality' of nozzles for directing the motive fluid onto the runner or wheel.

Another object of the invention is to provide a governor control which can operate automatically without any substantial supervision or can be operated manually from time to time as desired.

A still further object of the invention is to provide means for controlling in a predetermined fashion a plurality of nozzles effective upon a single prime mover.

A further object of the invention is, in general, to provide an improved governor control.

A further object of the invention is to provide a more nearly direct control of and feedback from the principal nozzle effective upon the prime mover.

The subject matter of the present invention can be incorporated in many dilferent ways depending upon the particular requirements of each installation but has been successfully embodied in connection with a multiple nozzle impulse turbine hydraulically impelled and mechanically connected directly to an electric generator. In the present situation, many of the governor parts and their functions are comparable to the parts and functions disclosed in the mentioned patents and application. In the device of the present description and shown in the accompanying drawings, all of the foregoing objects are attained, as well as others.

In the drawings, FIGURE 1A is a schematic diagram showing the left half of a layout of the present governor control; and

FIGURE 1B is the right half of the layout. When the left side of FIGURE 1B is adjoined to and aligned with the right side of FIGURE 1A, a complete diagram of the entire governor control is provided.

In the form of the structure treated herein, the shaft 6 of the rotating mechanism, including usually an electric generator and an impulse wheel 5, is directly connected to a small electric generator 7. By means of conductors 8 the generator 7 operates a motor 9 at a speed proportional to the shaft speed. Driven by the motor 9 is a ily ball governor 11 within a housing 12. The arrangement is such that the balls 13 of the governor spread apart with increase of speed and correspondingly lower a central governor valve core 14.

States Patent O The valve core 14 is effective to control certain governor hydraulic llow paths in a system separate and .apart from the hydraulic uid system utilized to drive the impulse wheel 5 connected to the shaft 6. For that reason, there is provided a source 16 of hydraulic fluid, such as oil, under substantial pressure. The oil is furnished through a conduit 17 and flows into a pipe 18 from which part of it passes through a pressure filter 19 and llows into a duct 21. A branch 22 of the duct 21 is connected by a pipe 23 to an isolating valve 24. In the position of the parts shown, which is for automatic governor operation, the isolating valve 24 is in such condition that ow through the pipe 23 is blocked.

The branch 22 also has a line 26 extending to a centrai passage 27 through a blocking valve 28. ln the position of the parts shown, flow continues from the line 26 through the passage 27 and is carried by a pipe 29 shunting a control relay 32.

Flow continues through the pipe 29 directly into a passage 34 in the housing 12. The pressure fluid cannot tlow directly from the passage 34 because of the momentary position of a valve spool 35 within the housing 12. When the governor speed increases, the balls 13 fly outwardly and the valve core 14 is lowered, thereby uncovering a passage 36 permitting llow of pressure lluid from the passage 34 through a partially uncovered port 37 in the housing 12 and thence outwardly through a conduit 38.

Connected to the conduit 38 is a port 39 in the control relay 32. The pressure fluid from the conduit 38 is effective to depress a piston 41 within the control relay 32. The piston 41 has a stem 42 followed by a lever 43 fast on a so-called B shaft 44. Since the drawing is diagrammatic, it is understood that the lever 43 and the `piston 41 always move together in unison. When the piston 41 descends under the initial, over-speed impulse of the governor 1`1 which produces the pressure ow in the conduit 38, the B shaft 44 is correspondingly and instantly rotated in a clockwise direction, as seen in the drawings. As hereinafter appears, there is substantially no hydraulic restraint on the movement of the piston 42. This immediate clockwise rotation lifts a lever 46 adjacent a secondary needle relay valve 47 and permits a spring 48 to lift a sleeve 49' so as to follow the lever 46.

The secondary needle relay valve 47 is provided with actuating hydraulic fluid under pressure from the pipe 18 through a branch pipe 50 opening into a port S1 in the valve 47. When the sleeve 49 lifts, pressure Huid from the port 51 flows into a duct 52 and through a connected pipe 53 to one end of a jet needle motor 54. This device is a hydraulic cylinder containing a reciprocable piston 56. The piston carries a nozzle needle 57 movable with respect to a jet orifice S8 and controlling hydraulic ilow therethrough onto the prime mover 5 on the shaft 6. When controlling lluid is admitted to the motor 54 at the right end of the piston 56, the piston and the needle 57 are moved to the left in the ligure, thus reducing the jet size. The jet reduction lessens the speed of the driven hydraulic wheel 5.

There is a feedback for the relay valve 47 from this positioning of the secondary needle 57. As especially shown in FIGURE 1B the secondary needle 57 is connected by a cable 131 to a quadrant lever 132 joined by a link i133 to a lever 92 at its center connected to a spool 93 in the secondary needle valve 47. When the secondary needle 57 is moved toward closed position, or to the left in FIGURE 1B, it correspondingly pulls the cable 131. This rotates the lever 132 clockwise and lifts the right end of the lever 92. Considering for the moment lthat the lever 92 has a stationary fulcrum point, the lever 92 is rotated counterclockwise and lifts the spool 93 so that the spool 93 is restored to its initial position relative to 3 the sleeve 49 and the secondary needle 57 is stopped in its new location. A similar compensating movement takes place in the opposite direction when the secondary needle is oppositely moved, the diagrammatically shown parts being effective in both directions of movement.

Movement of the piston 41 downwardly with increased governor speed not only lowers the stem 42 but also lowers an integral spool 62 within the control relay valve 32 and so uncovers a port 63. Pressure fluid from a conduit connected to the pipe 18 flows into the control relay 32 through a passage 31 and then flows through the port 63. Flow is then into a duet 64 connected through a passage 67 in the blocking valve 28 to a pipe 68. The end of the pipe 68 is blocked at the isolating valve 24 but a branch 69 extends from the pipe 68 to one end of a master needle motor 70. This device is a double acting hydraulic jack containing a reciprocable piston 71. The piston carries a master nozzle needle 72 movable with respect to a master jet orice 73 and controlling hydraulic ilow therethrough onto the prime mover 5 on the shaft 6. When controllin7 fluid is admitted to the master motor 70 at the right end of the piston 71, the piston and the master needle 72 are moved to the left in the figure, thus reducing the jet size. The jet reduction lessens the speed of the driven hydraulic wheel 5.

Pursuant to this invention movement of the master needle 72 is used directly as a governing factor. A counterweight cable 74 transfers movement of the master needle '72 in both directions to a drum 75 fastened to a so-called A shaft 76 having a number of controlling devices thereon.

As the piston 71 moves leftward under the influence of the pressure fluid arriving in the right-hand chamber of the master needle motor 70 because of increase in speed of the shaft 6, the A shaft 76 is correspondingly and directly rotated counterclockwise, as seen in the drawing. The rate at which the A shaft 76 rotates counterelockwise is directly governed by the speed at which the piston 71 moves to the left. The piston 71 in moving left dislodges hydraulic fluid from the chamber of the master needle motor 70 to the left of the piston and expels the oil through a conduit 77 extending to a passage 79 through the blocking valve 28. The conduit 77 is joined by a branch pipe 81 to the isolating valve 24 wherein it is blocked. From the passage 79, a line 82 extends to a port 83 in the control relay valve 32.

Since the integral spool 62 was previously depressed from the position shown when the governor immediately lowered the piston 41 upon over-speed, ow takes place through the port 83 and through the body of the valve and out through a port 86 therein. A variable restriction 87 controls the rate of etilux. The discharged fluid returns under low pressure to the supply mechanism 16 for recirculation. For simplicity herein, no flow return ducting is illustrated. Since the volumetric capacity of the master needle motor 70 is much greater than the volumetric capacity of the control relay valve 32, the restriction 37 serves to regulate the rate of leftward movement of the piston 71, although the restriction has little or no effect upon the rate of movement of the integral spool 62 within the control relay valve 32. In this fashion, the A shaft 76 is rotated counterclockwise at a controlled or regulated rate beginning with the motion of the piston 71 due to immediate B shaft response to the increase in prime mover speed.

Rotation of the A shaft 76 concurrently rotates a specially formed cam 91 (FIGURE 1B) controlling the movement of the lever 92 centrally connected to the spool 93 of the secondary needle relay valve 47. When the A shaft 76 rotates counterclockwise and places the cam 91 in a new lower position, the lever 92 at its left end follows the cam downwardly (the right end of the lever being momentarily considered as substantially fixed) and permits the spool 93 to descend.

The descending spool 93 allows pressure tiuid to flow through the duct 52 and the pipe 53 to close the needle 57. The feedback mechanism including the cable 131, responds as before to needle closing movement and causes a clockwise rotation of the quadrant lever 132 lifting the right end of the lever 92 thus lifting the spool 93 to closed position. Thus, in response to overspeed, the sleeve 49 promptly lifts to initiate needle closing movement and also, but at a slower rate, the spool 93 lowers to produce needle closing movement. The followup or feedback mechanism including the cable 131 in both instances restores the hydraulic pipe 53 to a no flow condition as soon as the needle 57 has attained its proper new, leftward position and without excessive response to the govcrnor change.

Appropriate feedback mechanism to the governor is provided. The countcrclockwise movement of the A shaft 76 is transmitted by a connector 101 to a clockwise rotated shaft i102 joined by a geared sector 103 to a gear wheel 104 having an indicator 106 thereon. The gear wheel 104 by its position is indicative of the load carried. This is usually marked as a percentage in apposition to the indicator 106. Clockwise rotation of the shaft 102 lowers a linkage having components 107 and 108 and changes the displacement conditions between an upper compartment 109 and a lower compartment 111 forming portions of a dash pot mechanism 112. A variable fulcrum 113 governs the amount of response of a plunger 114 in an upward direction. The ascending plunger 114 displaces liquid from the upper compartment 109 through an adjustable needle orilice 116 into the lower compartment 111. Since the liquid displacement is relatively slow, the volumetric difference is momentarily made up by the downward dislodgment of a spring centralized plunger i117, so lowering the left end of a compensating lever 118. Considering the right end of the lever 11S as being relatively stationary for the moment, the lowering of the left end thereof is effective through a link 119 to lower a follower lever 121 to which a valve cage 122 is attached. This cage surrounds the governor valve core 14 and has various ports therein.

Since the core 14 has previously been depressed by the ily balls 13 to follow the increasing speed of the governor 11, the valve cage 122 correspondingly descends with the lowering of the follower lever 121 and closes olf further flow through the conduit 33. There is thus provided a mechanical feedback to the governor directly from the "A shaft 76 and directly from the master needle 72 without any delay except for the dash pot 112.

Not only is there a feedback to the governor from the A shaft 76 which responds directly to the movement of the master needle 72, but iikewise there is a feedback to the governor from the B shaft 44. An upstanding lever 136 (FIGURE 1B) on the B shaft is connected by a link 137 to a quadrant 138. When the B shaft 44 rotates clockwise, the quadrant 13B also rotates clockwise and similarly rotates a variablelength lever 139 having as its fulcrurn the shaft of the quadrant 133. This permits an abutting lever 141 to lower a link 142 and correspondingly to lower the right end of the lever 113. The valve cage 122 is thus moved downwardly to close on? further ow through the conduit 38.

rhe foregoing cycle is the one that occurs when the governor responds to over-speed and is effective to restore the parts substantially to their original condition after a suitable corrective closing movement of the master nozzle needle 72 and of the secondary needle nozzle 57.

A substantially comparable but opposite chain of circumstances ensues when the load on the water wheel in* creases sufficiently to reduce its speed. rfhen the balls 13 move toward each other and thus lift the valve core 14. Pressure fluid from the passage 34 then flows upwardly around the valve cure 1d und [in-ries out :i port 151 into a conduit 152 which joins the control relay vulve 32 in a port 153. The piston 4l is then lifted, immediately rotating the "il" shaft 44 in a countcrclockwise direction and simultaneously shifting the integral spool 62 so that pressure fluid from the conduit 30 and the port 31 passes out the port 83 and through the line 82 and the conduit 77 into the master needle motor 70 to the left of the piston 71. This piston is then moved to the right to increase water flow although relatively slowly since the discharge of liquid from the volume to the right of the piston through the conduit 69 is throttled by ai variable restriction 154 connected to the outlet port 156 of the valve 32. Thus, the B shaft 44 is quickly rotated in a counterclockwise direction, and the A shaft 76 is also rotated but in a clockwise direction only at a controlled rate directly in response to the more deliberate movement of the master needle 72.

When the B shaft 44 rotates counterclockwise as the stem 42 rises, the lever 46 depresses the sleeve 49 so that pressure fluid from the branch pipe 50 flows around the spool 93 and out through a conduit 161 into the secondary cylinder 54 to the left side of the piston 56. This has the effect of withdrawing the secondary needle 57 from the jet orifice 58 and permitting a greater flow of hydraulic fluid to impinge upon the water wheel. The rate of movement of the secondary piston 56 is governed in both directions by variable restrictions 162 and 163 disposed in the outlets from the secondary relay needle valve 47. The movement of the B shaft 44 in the counterclockwise direction is transmitted to the valve cage 122 by means of the link 137 and the associated mechanism, while the new open position of the secondary needle 57 is made effective upon the spool 93 by appropriate motion of the cable 131 and the associated relay valve feedback mechanism.

The opening movement of the master needle 72 rotates the A shaft 76 at the set rate in a clockwise direction and through the cam 91 lifts the spool 93 to cause hydraulie fluid flow into the conduit 161 to urge the nozzle needle open. The needle opening movement, through the feedback mechanism including the cable 131, correspondingly lowers the right end of the lever 92 and so lowers the spool 93 to shut off position when the needle 57 attains its new open position.

The clockwise rotation of the A shaft 76 directly responsive to opening movement of the master needle 72 under the increased load and decreased speed is also transferred directly by the connector 101 to the shaft 102 and produces a direction of movement of the interconnecting linkage opposite to that previously described to impose a correcting movement on the valve cage 122.

Means are provided for limiting the amount of load that can be assumed by the hydraulic wheel 5. This is accomplished by limiting the amount that the master needle '72 and the secondary needle 57 may open. This can be called a maximum nozzle orifice control or is sometimes called a load limit control. As shown in FIGURE 1A, a hand regulator 171 suitably positions a geared disk 172 having an appropriate indicator 173. This indicator usually is graduated in percent of total travel of the master needle 72 and is illustrated in approximately fifty percent of total travel position.

A pin 174 on the disk 172 adjusts the position of one end of a lever 176, the other end of which is engaged with a pin 177 on the gear wheel 104. Centrally of the lever a link 178 is fastened and is also joined to a lever 179 on a shaft 181. Another lever 182 on the shaft 181 is connected by a strap 183 to a lever 184, at its remote end connected `by a link 186 having a lost motion connection therein to the pinned end of a lever 187 on the quadrant 138. Between its ends, the lever 184 is joined to a valve spool 188 urged upwardly by a spring 189 and interposed in the flow paths from the valve cage 122.

When the hand regulator 171 is operated so as to turn the disk 172 counterclockwise, for example, to reduce the maximum permissible orifice opening, the lever 176 is raised at its right end and lifts the link 178. Through the shaft 181, the strap 183 is lowered and depresses the left end of the lever 184. When the lost motion in the link 186 has been taken up, the spool 188 is lowered. This permits pressure fluid from the passage 34 to travel out of the port 37 and through the conduit 38 into the port 39 of the control relay valve 32, depressing the spool 62 therein. This permits hydraulic pressure fluid to flow through the conduits 64 and 69 to the right end of the master motor 70 and to move the master needle 72 toward closed position thus reducing hydraulic flow through the master orifice 73 and rotating the A" shaft 76 counterclockwise. The lowering motion of the stem 42 also causes clockwise rotation of the B" shaft 44, permits the sleeve 49 to lift and so permits flow of pressure fluid from the branch pipe 50 into the pipe 53 and urges the secondary needle 57 to the left, thus reducing hydraulic flow through the secondary nozzle 58, the feedback including the cable 131 operating as before to lift the spool 93 to hold the new needle position.

The other actions of the associated mechanisms take place as before so that when the maximum permissible orifices are reduced, the A and B shaft motions through the governor feedback mechanisms, particularly the link 137 as well as the connector 101, produce a compensating counterclockwise rotation of the gear wheel 104 and a repositioning of the lever 176 by lowering the left end thereof. Also there results a rotation of the quadrant 138 and a repositioning of the lever 184 and the spool 18S. Thus, when the maximum orifice opening or load limit is reduced, the needles are correspondingly moved toward closed position and when they have attained the newly set more nearly closed position the parts are again in equilibrium. Substantially the revers-e scquence of events occurs when the load limit or maximum opening is increased by rotation of the geared disk 172 in a clockwise direction.

Means are provided for varying the set speed at which the governor particularly responds. A control knob 191 is connected to a geared disk 192 having an indicator 193 usually gradluated in percentage of nominal speed, the indicator illustrating one hundred percent nominal speed in FIGURE lA. On the disk 192 there is provided a pin 194 connected by a connector 196 to a lever 197 on a shaft 198. Also on the shaft is a lever 199 connected by a link 201 to a lever 202, at its right end pivoted to the lever 121.

When the control knob 191 is turned to revolve the disk 192 counterclockwise, for example, to increase the set speed of the unit, the connector 196 rotates the shaft 198 counterclockwise also and pulls the link 201 down. Assuming the left end of the lever 202 is a fixed pivot, the right end of the lever 202 is then depressed. Assuming further that the right end of the lever 121 has a fixed pivot, then the valve cage 122 is lowered. This has the effect of admitting pressure fluid from the passage 34 to flow out the port 151 and to travel through the conduit 152 and to raise the piston 41 of the control relay valve 32. This permits hydraulic fluid to move the master piston 71 to the right thus opening the master orice 73 and rotating the A shaft 76 clockwise and with feedback as previously described through the link 101. The rising piston 41 also revolves the B shaft 44 quickly in a counterclockwise direction and lowers the sleeve 49, thus admitting pressure fluid to the conduit 161 and opening the secondary orifice S8 with B shaft governor feedback as described previously through the link 137. A new position for the valve cage 122 and the nozzle needles is thus provided. The speed can be reduced simply by reverse rotation of the control knob 191. This is followed by motions of the parts in directions opposite to those previously described.

Under some circumstances, it is desired that the governed speed not remain precisely fixed or as set by the knob 191 at a predetermined value but that the speed of the mechanism be permitted to decrease some established amount from the assigned value under increasing load. The decrease in speed under increasing load is referred to as speed droop. Under some conditions, the speed is made to increase under added load and this is referred to as negative speed droop. With the mechanism as shown in the position of FIGURE 1A and as so far described, there is no speed droop possible and the speed of the mechanism is maintained at a set value under the permissible load. However, if speed droop is desired, it can be provided in an adjustable amount.

A control knob 211 operates a geared disk 212 which is provided with an indicator 213 usually graduated in percentage of normal speed. If the speed droop is to be increased, the knob 211 is turned so as to rotate the geared disk 212 in a counterclockwise direction. Through a flexible push-pull cable 214 this produces a corresponding drop at the left end of a lever 21.5 fast on a shaft 216. A fork lever 217 on the shaft 216 is moved counterclockwise and by engagement with a rod 21S translates a roller 219 on the rod to the right along an inclined ramp 221.

The ramp is located at a position tangent to a circle of the diameter of the roller end concentric with the rotation-.fil center of a lever 222 on which it is mounted. The lever is pivotally supported in a location between the ends of the ramp 221 and by suitable pivot connections is interposed between the links 167 and 10S. The roller 219 is translated along the ramp by swinging of the forked lever 217. One of the various positions of the roller 219 coincides exactly with the pivotal or rotational center of the lever 222 while the other roller positions are displaced therefrom in various amounts. The rod 218 which carries the roller 219 also is connected to a link 223 joined to the lever 202.

When the lever 215 is rotated counterclockwise, the fork lever 217 is likewise rotated counterclockwise and the roller 219 is rolled to the right along or down the ramp 221 and so is displaced from the rotational center of the lever 222. When the roller is so displaced, any motion of the lever 222 accompanying the motions of the links 107 and 10S is effective to displace the link 223. When the roller 219 is concentric with the lever 222, motion of the links 167 and 108 does not affect the link 223. So that the lever 292 in effect has a fixed pivot at its left end and under these circumstances, there is no speed droop. However, when the roller 219 is displaced on the ramp, say to the right, then when there is motion of the links 107 and 108 a corresponding rotation of the lever 222 occurs and motion is given to the link 223. This produces motion of the lever 262 and also of the lever 121, thus readjustng the valve cage 122 correspondingly and permitting the master needle 72 and the secondary needle 57 to close somewhat more than would be the case under a no-droop regulation. A displacement of the roller off center to the left similarly affords negative speed droop.

The governor controlling mechanism of the invention is satisfactorily usable with only a master nozzle and needle combination but is most often used in connection with an impulse turbine having a plurality of nozzles and needle controls. It has therefore been described herein up to this point as having a master nozzle and needle and also one additional or secondary nozzle and needle. But often in larger installations there are even further nozzles and needles used. Hence this disclosure includes a tertiary nozzle and needle combination intended to represent any additional number of such combinations. Mounted on the A" shaft 76 is a cam 231 (FIGURE 1B) somewhat similar in shape to the cam 91 but having a suiciently diierent contour so that the control functions resulting from the operation of the cams are of the desired relative characteristics.

The cam 231 bears against the roller end of a lever 232 connected between its ends to a valve spool 233 extending into the housing oi a tertiary needle relay valve 234. The valve 234 is identical interiorly with the secondary valve 47 and is connected by a conduit 236 to the pipe 1S. Within the housing of the valve 234 there is an inlet passage 237 controlled by the spool 233 to allow pressure fluid to ilow either to a closing conduit 23S or to an opening conduit 239. Suitable restricted outlets 2*.1 and 242 serve to control the rate of operation of a piston 243 contained in a tertiary needle motor cylinder 244. The piston 243 is provided with a tertiary needle 246 effective by its position to control the rate of ow through a tertiary orifice or nozzle 247. The jet issuing from the nozzle 247 impinges upon the same turbine as do the iets from the master and secondary jet orifices 73 and 58.

ln a fashion comparable to that utilized in connection with the secondary valve l417, the B" shaft 44 is provided with a lever 251 effective upon rotation of the B shaft to produce a corresponding motion of a valve sleeve 252 encompassing the spool 233 and assisting in the control of fluid low through the valve housing 234. A spring 253 is interposed between the spool 233 and the sleeve 252 so that they move appropriately relative to each other.

There is a valve feedback structure responsive to the movement of the tertiary needle 246. 'This includes a cable 256 extending from the needle to an arcuate lever 257 provided with an appropriate fulcrum 253. At its opposite extremity the lever 257 is connected by a link 259 to the right-hand end of the lever 232. The effect of the lever structure 251 is to cause motion of the sleeve 252 immediately upon operation of the B shaft 44. The sleeve motion is followed by an appropriate, more deliberate motion of the spool 233 in response to the motion of the cam 231 on the A shaft 76. These actions of both the sleeve and the spool are compensated for by the feedback motion from the tertiary needle 246 which causes corresponding motion of the lever 232.

By appropriately positioning the cams 91 and 231 on the A shaft 76 and by appropriately contouring the cams, and further by appropriately adjusting the various discharge restricting devices, such as 162 and 163 as well as 241 and 242, the sequential or relative operation of the two needles 57 and 246 can `be precisely controlled not only with regard to each other but also with regard to the master needle 72 which moves according to its own restrictions 87 and 154. By programing the operation of the described needles and of any others provided with comparable controlling mechanism, it is possible to operate a multi-jet turbine at a substantial improvement in efficiency and in load-carrying ability over presently known systems.

While the governor controller mechanism for varying the position of the needles is effective under most ordinary circumstances, the needles must necessarily, because of surrounding mechanisms, move more slowly than the occurrence of some unusual event. For example, there may be a `failure in the electric line leading from the generator driven by the hydraulic turbine 5 on the shaft 6. This is a sudden removal of all load. The nozzle needles because of hydraulic flow requirements cannot be permitted to respond quickly enough suddenly to shut down the hydraulic turbine, and hence other means are provided for avoiding excessive ovcrspeed and consequent damage. For that reason, each of the nozzles, such as 5S, 73 and 247, is provided with its own deilector, such as 260, 261 and 262, having pivot mountings 263. As so mounted, the detlectors 261), 261 and 262 are normally positioned just outside of the water jets issuing from the nozzles 73, 58 and 247 but can very quickly move into position to intercept the jets and to divert them from the hydraulic wheel so that the rotating machinery does not seriously over-speed. Preferably, the three (or more) deflectors 260, 261 and 262 are connected together by mechanical connections 264 and 265 so that they always move in unison. While the deilcctor moving mechanism can be l mechanically duplicated for each jet, it is usually economically advantageous to provide all of the detlectors with one actuator located in any convenient position and serving to operate all of them in unison.

A suitable actuator includes a piston 266 operating within a motor cylinder 267 and connected by a piston rod 268 to the connections 264 and 265 for moving the deflectors. Appropriate motion is given to the piston 266 by hydraulic means. A branch conduit 269 `from the pipe 18 joins a decctor control relay valve 270 at an appropriate port 271 leading into a valve spool chamber 272. Flow through the chamber 272 is controlled by a valve spool 273 on a stem 274 extending upwardly out of the housing of the valve 270.

When the valve spool 273 is in the position shown in FGURE 1B, there is no ow to the motor cylinder 267.

When the valve spool 273 is lowered, there is pressure huid ow through the chamber 272 into a hydraulic conduit 276 leading into the right-hand end of the motor cylinder 267, and effective to move the deflectors 260, 261 and 262 into intercepting position. Return flow for the fluid then discharged from the left end of the motor cylinder 267 is through a conduit 277 and back through the chamber 272 and out a discharge port to the sump or reservoir (not shown).

When the valve spool 273 is in an uppermost position, the connection of the branch conduit 269 is then directly to the conduit 277, producing a motion of the piston 266 to the right in FIGURE 1B, thus withdrawing the deflectors from an intercepting position. Under these circumstances, the return fluid from the right end of the motor cylinder 267 Hows `back through the conduit 276 and out of the valve housing 270 to the reservoir or sump. The valve spool 273 is under the control of a servo mechanism 27S operated by hydraulic fluid conducted to the valve housing 270 through a conduit 279 extending from the filter 19 and controlled by a translatable valve spool 280 and a valve sleeve 281. The spool and the sleeve are appropriately urged relative to each other by an interposed spring 282.

Motion of the spool 280 is derived primarily from the A shaft 76 and the B shaft 44. The A shaft 76 at one end carries a suitably contoured cam 286 acting against a `follower 287 connected to one end of a iioating link 288. The end of the B shaft 44 carries a lever 289 joined by a link 291 and a bell crank 292 to the other end of the link 288. A hanging link 293 depending from the link 288 is connected at the other end to a lever 294 between its ends joined to the valve spool 280.

When an excessive over-speed occurs, the governor 11 immediately moves the governor valve core 14 downwardly in a substantial amount and permits pressure Huid to flow through the conduit 38 to depress the piston 41 quickly and to rotate the B shaft 44 a substantial amount in a clockwise direction. 'Ibis drops the link 293 and depresses the left end of the lever 294 to lower the valve spool 280. Pressure fluid from the conduit 279 is thus permitted to flow immediately into the upper end of the servo mechanism 278 and to lower the valve spool 273. Then, pressure fluid from the conduit 269 flows into the conduit 276 and immediately drives the piston 266 to the left in FIGURE 1B, promptly interposing the deflectors into the several hydraulic jets.

The downward motion of the piston 41 which rotates the B shaft 44 initially, by altering the hydraulic flow to the master cylinder 70 also causes movement of the piston 71 but at a relatively slow rate. This movement is toward the left and rotates the A shaft 76 in a counterclockwise direction almost simultaneously with the rotation of the B shaft 44. Rotation of the A" `shaft 76 rotates the cam 286 in a counterclockwise direction, lifts the left end of the link 288, lifts the hanging link 293 and lifts the valve spool 280 `from its previously lowered position. This permits fluid to flow into the servo 278 to lift the stern 274 and so lifts the valve spool 273. The piston 266 is moved to the right and pulls the deflectors 26|), 261 and 262 away from the jets. The movement of the valve spool 273 under the action of the servo 27 8 correspondingly moves a levez 301 bearing upon the valve sleeve 281 and forming part of a servo feedback so that the sleeve 281 follows the motion of the stem 274 and tends to stop the action which Vthe initial movement of the spool 280 has started.

During normal operation, the foregoing structure moves the deflectors to follow just outside the varying jets and acts to hold them out during proper operation.

But when gross over-speed occurs, the "5 shaft 44 lowers the valve spool 286 and through the servo 278 shifts the valve spool 273 to move the piston 266 to the left, thus interposing the dellectors 261 and 262 in the jets. The dellectors are always in position so that they can be very quickly interposed in the jets dvet under normal operations do not in any wise interfere with the efflux ofthe water.

A feedback mechanism is provided for the deilectors. Connected to the piston rod 268 is a cable 302 extending to an arcuate lever 303 having a suitable fulcrum 304 and connected by a link 306 to a rocking lever 3d?. This lever, having a fulcrum 308, is connected to the plunger 369 of a dash pot mechanism 311 quite comparable to the dash pot mechanism 132. The plunger 389 operates to displace hydraulic liquid between a lower chamber 312 and an upper chamber 313, the displacement rate being controlled by a needle regulator 314. Excessive hydraulic liquid in either of the chambers is effective correspondingly to displace a spring centered piston 316 connected to the right end of the lever 294.

lf the dellectors 268, 261 and 262 move at an excessive or at a deficient rate as established by the regulator 314, there is a momentary excess of hydraulic fluid in one or the other of the chambers 312 and 313 and the piston 316 is correspondingly displaced. 'This either lifts or lowers the right end of the lever 294 and produces a corresponding and correcting displacement of the valve spool 280. There is consequently provided with this mechanism a controller responsive to the governor primarily, and effective to interpose deflectors in the various jets in accordance with a controlled program.

While automatic operation is utilized virtually all of the time in accordance with the disclosure and description herein, there are certain instances, for example, for `tests and special operation, wherein control is best carried out manually. Under those circumstances, it is desired to have means for disabling much of the automatic control structure.

As particularly shown in FIGURE lA, the duct 21 is provided with a branch 321 extending to a transfer valve housing 322. A rotary valve 323 is normally in the position illustrated and conducts ow to an outlet conduit 324 extending to a chamber 32S in the bottom of the isolating vulve 24. Pressure from the conduit 324 is effective to urge a valve spool 326 upwardly in the housing 24 against the urgency of a spring 327. The spool 326 is thus normally held in the blocking position illustrated so that there is no active flow through the housing 24.

A conduit 328 extends from the transfer valve housing 322 and is connected to a port 329 in the blocking valve housing 28. Pressure from the conduit 328 is effective to depress a piston 331 in the housing 28 against the urgency of a spring 332 so that the valve stern 333 on which the piston 331 is situated is normally held in its open and free-flow position. This is the arrangement for automatic operation.

When manual operation is to ensue, the rotary valve 323 is revolved clockwise through substantially ninety degrees. This blocks the `branch 321 and connects the conduits 324 and 328 to a drain conduit 334 extending to the reservoir or sump. Nhen this occurs, the pressure drops and the spring 327 immediately lowers the valve spool 326, thus opening all of the ports in the isolating ses-1,900

ftlve housing 24. At the same time, the drop in pressure Within the top of the chamber in which the piston 331 operates is suthcient so that the spring 332 lifts the vulve stem 333, thus blocking llovv through all of the ports in the blocking valve housing 28. Furthermore. the valve stem 333 in lifting abuts un adjustable arm 335 on the shaft and if necessary rotates the "B shaft counterclocltwise or in any case holds the shaft in a selected central position. This holds the valve spool o2 und keeps the master needle 7'?. stationary and holds the secondary needle relay vulve 47 with its sleeve or enge #t9 in a fixed position and also holds the sleeve or caffe 252 of the tertiary needle relay valve 234 in tiXcd posi ion.

With this position of the mechanisms 24 and 28, thc main control is by hand manipulation of the hand regulator ll'l. This causes motion ofthe lever 176 and of thc link 179, to revolve the shaft 131 correspondingly. A lever 341 on the shaft llll moves valve core 342 within the housing 24 and against a spring 3dS. Motion of the core 342 controls tlow from the pipe 23 into either of the pipes del or Si. Return ilow from either of those pipes is directed by the core 342 into a discharge line 344 lending back to the hydraulic sump. The pipes 68 and El, being joined to the conduits 69 and 77, respectively, operate the piston '7l and so the needle 7.2 and rotate the A shaft 76 to move the valve spools 93 and 233 and so move the needles 7 and 246. Any needle position can thus be manually attained with the aid of the hydraulic system and the r shaft.

v'ith thc mechanism described herein it is possible to secure good speed and load response and regulation with :t plurality of jets and detlcctors. Upon the occurrence of ovcrspced, for example, the B shaft moves accordingly and almost instantly. This response is at a precetermincd rate, although the range or amount of "B" shaft movement is not great since the ilyhulls 13 malte only small excursions from steady state position in order to assure close regulation. Consequently, the sleeves, such as 49, move promptly at a predetermined rate but only through relatively short distances. The t3 shaft motion, even though slight, by reason of valve spool 62 in the control relay valve 32 initiates a corresponding but slower motion of the A shaft. The longer the "13 shaft is out of steady state position, the farther the 1V shaft moves from its own steady state position and the more the spools, such as 93, are moved to afford an appropriate compera tion.

What is claimed is:

l. A governor' control comprising a master nozzle needle, another nozzle needle. a master hydraulically actuated means including u master hydraulic valve for positioning said master needle, another hydraulically actuated means including another hydraulic valve having u spool and a sleeve for positioning said other needle, means responsive at n predetermined rate to speed for actuating said master hydraulic valve and said sleeve, and means responsive to the position of said master needle for actuating said spool at a different. rate.

2. A governor control comprising a master nozzle needle, n master hyd rnulic motor for actuating said master needle, a master hydraulic circuit cor ctcd to said master motor, n master valve in said circuit having a movable master sool, means responsive to speed, means actuated by said responsive means for movin" said master spool at a predetermined rate to control s master circuit, snother nozzle needle, another hydraulic motor for actuating said other needle, another hydraulic circuit connected to said other motor. another vulve in said other circuit having another movable spool and a movable sleeve in series` means actuated by said responsive means for moving sn' sleeve st a predetermined rate to control said other ciruit, and means actuated by said muster needle for moving said other spool at a ditlcrcnt rate to control said other circuit.

3. A governor control coutprising a muster means and lel) another means movable into diierent positions to control speed, master hydraulic means and other hydraulic means for respectively moving said master means and said other means, a master hydraulic circuit for said master means, a muster vulve in said master hydraulic circuit for controlling said master circuit, another hydraulic circuit for said other means, another valve in said other hydraulic circuit for controlling said other hydraulic circuit, said other valve including a first member and a second memher in series for so controlling said other hydraulic circuit, means responsive to said speed, means controlled by said responsive means for operating aid master valve and said tirst member at a predetermined rate, and means controlled by said master hydraulic means for operating said second member at a diifclcnt rate.

4. A governor control comprising a master means movable into different positions to control speed, master hydraulic means for moving said master movable means, a muster hydraulic circuit for said master hydraulic means, a master valve in said master hydraulic circuit for Controlling siad master circuit. another means movable into different positions to control said speed, other hydraulic means for moving said other movable means, another hydraulic circuit for said other hydraulic means, another valve in said other hydraulic circuit including a iirst device and a second device in series for controlling sai'd other circuit, means responsive to said speed, means controlled by said responsive means for operating said master valve and said first device sinuiltaneously, and means controlled by said master means for operating said second device according to the operation of said master means.

5. A governor control comprising a plurality' of nozzle needles individually movable to control speed, individual means for moving euch one of said nozzle needles, means responsive to said speed, means actuated by said speed responsive means for controlling said movingY means for one of said nozzle needles, and means including a plurality of cams movable in unison in response to movement of said one of said nozzle needles for operating the others of said individual moving means, said cams each being connected to operate a respective one of said others of said individual moving means.

6. A governor control comprising u master nozzle necdle and u plurality of other nozzle needles individually movable to control speed, individual means for controlling each one of said master and said other nozzle needles, n com shaft, individually different cams on said com shaft, means for making each one of said cams effective upon n different one of said controlling means for said other nozzle needles, means responsive to said speed for actuating said controlling means `for said master nozzle needle, and means for rotating said cam shaft in response to the movement of said master nozzle needle.

7. A governor control comprising a master nozzle needle and a plurality of other nozzle needles individually movable to regulate water Yiets to control speed, individual means for controlling each one of said nozzle needles, a cam shaftA individually different cams on said cam shaft, means for mailing each one of said cams effective upon a direrent one of said controlling means for said other c needles, means responsive to said speed for actuating said controlling for said master nozzle needle. means for rotat said cam shaft in response to the movement ol said mater nozzle needle. a plurality of dei'lectors, means for simultaneously moving all of said deflcctors into all of said water iets, and a special. cam on said com shalt for controlling said dellector moving means.

References Cited in the File of this patent UNTED STATES PATENTS 2 53,193 Dcgion May 16. i938 2.398.925 Avery Aug. ll, i959 2,965,764 Nichols Dec. 2U, 19o()

Claims (1)

1. A GOVERNOR CONTROL COMPRISING A MASTER NOZZLE NEEDLE, ANOTHER NOZZLE NEEDLE, A MASTER HYDRAULICALLY ACTUATED MEANS INCLUDING A MASTER HYDRAULIC VALVE FOR POSITIONING SAID MASTER NEEDLE, ANOTHER HYDRAULICALLY ACTUATED MEANS INCLUDING ANOTHER HYDRAULIC VALVE HAVING A SPOOL AND A SLEEVE FOR POSITIONING SAID OTHER NEEDLE, MEANS RESPONSIVE AT A PREDETERMINED RATE TO SPEED FOR ACTUATING SAID MASTER HYDRAULIC VALVE AND SAID SLEEVE, AND MEANS RESPONSIVE TO THE POSITION OF SAID MASTER NEEDLE FOR ACTUATING SAID SPOOL AT A DIFFERENT RATE.

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