US3110472A - Governor controller - Google Patents

Description

Nov. 12, 196.3 P. B. DAwsoN, JR., ETAL 3,110,472

GOVERNOR CONTROLLER Filed Aug. 7, 1959 2 Sheets-Sheet l y FIG -IA Avrai/Vini Nov. 12, 1963 P. B. DAwsoN, JR., ETAL 3,110,472

GOVERNOR CONTROLLER Filed Aug. 7, 1959 2 Sheets-Sheet 2 .sv/PPD v v mi( United States Patent() 3,110,472 GOVERNR CNTROLLER Percy B. Dawson, Jr., (kinda, and Byron E. Wheeler,

Burlingame, Calif., assignors to Baldwin-Lima-Hamilton Corporation, a eorporation of Pennsylvania Filed Aug. 7, 1959, Ser. No. 832,312 7 Claims. (Cl. 253--24) Our invention relates to devices especially concerned with speed and o-ther related controls of relatively large hydraulic propulsion machinery of the sort utilizing an Iimpeller 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 lwater emerging from nozzles controlled by `axially movable needles. A device of this general nature is shown in Patent 2,767,938 issued May l0, 1955, to the assignee hereof and in Patent 2,857,885 issued October 28, 1958, to the assignee hereof.

An object of the 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 loa-d on the unit and despite certain other variations in operating circumstances. f

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

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 eiective upon a single prime mover.

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

The subject matter of the present invention can be incorporated in many different ways depending upon the particular requirements of each installation but has been successfully embodied in connection with Ia 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. 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 controller; and

FlGURE 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 controller is provided.

In the form of the structure treated herein, the shaft 6 of the rotating mechanism, including usually yan electric generator and an impulse Wheel 5, is Adirectly connected to a small electric generator 7. By means of conductors 8 the generator 7 operates a motor 9 at a speed proportion-al to the shaft speed. Driven by the motor 9 is a fly 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 ya central governor valve core 14.

The valve core 14 is effective to control certain governor hydraulic llow paths in a system separate and apart from the hydraulic fluid system utilized to drive the impulse wheel 5 connected to the shaft 6. For that reason, as shown in FIGURE 1B, there is provided a source 16 of hydraulic iluid, 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 ilo-ws int-o -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 ilow through the pipe 23 is blocked.

The branch 22 also has a line 26 extending to a central passage 27 through a blocking valve 28. In the position of the parts shown, llow continues from the line 26 through the passage 27 and is carried by a pipe 29 to a passage 31 through a control relay 312.

In the position of the parts shown, llow continues through the passage 31 and through a conduit 33 into a passage 34 in the housing 12. The pressure fluid cannot flow 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 ly outwardly and the valve core 14 is lowered, thereby uncovering a passage 36 permitting flow of pressure fluid 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 3S 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 stern 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 11 lwhich produces the pressure flow in the conduit 38, the B shaft 44 is correspondingly and instantly rotated in a clockwise direction, as seen in the drawings. This clockwise rotation lifts a lever 46 adjacent a primary needle relay valve 47 and permits a spring 48 to lift a sleeve 49 so as to follow the lever 46.

The primary needle relay valve 47 is provided with actuating hydraulic fluid under pressure from the pipe 18 through a branch pipe 5t) opening in-to a port 51 in the valve 47. When the sleeve 49 lifts, pressure lluid from the port 51 ows 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 58 and controlling hydraulic llow therethrough into 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 primary needle relay valve 47 from this positioning of the primary needle 57. As especially shown in FIGURE 1B the needle 57 is connected by a cable 131 to a quadrant lever 132 joined by a link 133 to a lever 92 at its center connected to a spool 93 in the primary needle relay valve 47. When the 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 that the lever 92 has a stationary fulcrurn 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 the sleeve 49 and the needle 57 is stopped in its new location. A similar compensating movement takes piace in the opposite direction when the primary needle 57 is oppositely moved, the diagrammatically shown parts being effective in both directions of movement.

Movement of the piston 41 downwardly 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 the passage 31 thus flows into a duct 64 connected through a passage 67 in the blocking valve 2S to a pipe 63. The end of the pipe 63 is blocked at the isolating valve 24 but a branch 71 extends from the pipe 63 to the upper chamber of a cam control servo 72. Pressure iluid from the conduit 71 is effective on the upper side of a movable piston 73 connected to a crank 74 fastened to a so-called A shaft 7d having a number of controliing devices thereon.

As the piston 73 descends under the influence of the pressure fluid arriving in the upper chamber of the cam control servo 72 because of increase in speed of the shaft 6, the A shaft 7d is correspondingly rotated counterclockwise, ask seen in the drawing. The rate at which the A shaft 76 rotates counterclockwise is governed by the speed at which the piston '73 can descend. The descending piston 73 dislodges hydraulic fluid from the chamber of the cam control servo 72 beneath 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 when the governor immediately lowered the piston 41 upon over-speed, flow takes place through the port 83 and through the body of the balve and out through a port 86 therein. A variable restriction S7 controls the rate of etllux. 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 cam control servo 72 is much greater than the volumetric capacity of the control relay valve 32, the restriction S7 serves to regulate the rate of descent of the piston 73, although the restriction has little or no effect upon the rate of movement of the integral spool 62 within the control relay valve 32. ln this fashion, the A shaft 76 is rotated counterclockwise at a controlled or regulated rate shortly after the governor 11 has caused the B shaft to respond 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 primary needle relay valve 417. When the shaft 76 rotates counterclockwise and places the cam '5'1 in a new 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. K

The descending spool 93 allows pressure fluid 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 over-speed the sleeve 4% 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 governor change.

Appropriate feedback mechanism to the governor is provided. The counterclockwise movement of the A shaft 76 is transmitted by a connector 101 -to a shaft 162 joined by a geared sector 163 to a gear wheel 104 having an indicator 166 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 1%. Clockwise rotation of the shaft 102 lowers a linkage having components 11W and 168 and changes the displacement conditions between an upper compartment 169 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 orifice 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 117, so lowering the left end of a compensating lever 11S. Considering the right end of the lever 118 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 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 off further iiow through the conduit 33. There is thus provided a mechanical feedback to the governor from the A shaft 7d.

Not only is there a feedback to the 'governor `from the relatively slowly moving A shaft 76, but likewise there is a feedback to the `governor from the relatively rapidly moving B shaft 44. An upstanding lever 136 on the B shaft is connected by a link 137 to a quadrant 138. When the B shaft 44 rotates clockwise, the quadrant 138 also rotates clockwise and similarly rotates 'a variable length lever 139 having as its `fulcruim the shaft of the quadrant 13S. This permits an abutting lever 141 to lower `a link 142 and correspondingly to Ilower the right end of lthe lever 118. The valve cage 122 is thus moved downwardly to close off further flow through the conduit 38.

The foregoing cycle is lthe 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 needle nozzle 57.

A substantially comparable chain of circumstances ensues when the load on the water wheel increases sufficiently to reduce its Speed. Then the balls 13 move toward each other and thus lift the valve core 14. Pressure uid from the passage '34 then ilows upwardly around Vthe valve core 14 and passes out a port 151 into `a conduit 152 which joins the control relay valve 32 `in `a port 153. The piston 41 is then lifted, immediately rotating the B shaft 44 in a counterclockwise direction and simultaneously shifting the integral spool 62 so that pressure fluid from the conduit 33 passes out the port `il?) and through the line 32 and the conduit 77 into the cam control servo '7Z`beneath the piston 73. This piston is then lifted relatively slowly since the :discharge of liquid from the volume above the piston through the conduit 71 is throttled by a variable restriction 154 :connected -to the outlet port 156. Thus, while the B shaft 4d is quickly rotated in a counterclockwise direction, the A shaft 76 is only slowly rotated in a clockwise direction.

-Jhen 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 Sii flows around the spool 93 and out through a conduit 161 into the cylinder S4 to the left `side of the piston 56. This has the effect of withdrawing the 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 piston 56 is governed in both directions by variable restrictions 162 and 163 disposed in the outlets from the primary 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 needle 57 is made effective upon the spool 93 by appropriate mo-tion of the cable 131 and the associated mechanism.

The upward, opening movement of the piston 73 rotates the A shaft 76 at the set rate in a clock-wise `direction and through the cam 91 `lifts Ithe spool 93 to cause hydraulic fluid ow into the conduit 161 to urge the nozzle needle 57 open. The needle yopening movement, through the feedback mechanism including the cable 131 corresponding lowers the right end of the lever 92 `and so lowers the Spool 93 to shutoff position when the needle 57 attains its new open position.

The relatively slow clockwise rotation of the A shaft 76 under the increased load and decreased speed is transferred by the connector 101 to the shaft 1112 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 provi-ded for limiting the amount of load that can be assumed by the hydraulic wheel 5. This is accomplished by limiting the amount that the needle 57 may open. This can be called a maximum nozzle orifice control or is sometimes cal-led a load limit control. As shown in FIGURE 1A, a hand regulator 171 suitably positions a geared Idisk 172 having an appropriate indicator 173. This indicator usually is graduated in percent of total travel of the needle 57 and is illustrated iu approximately fifty percent of total travel position.

A pin 174 on the disk 172 adjusts the position or 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 134, `at its remote' end connected by a link 186 having a lost motion connection therein to the pinned end of a lever 1157 on the quadrant 138. Between its ends, the lever 134 is joined to a valve spool 188 urged upwardly lby a spring 189 'and interposed in Ithe flow paths from the valve cage 122.

When the hand regulator 171 is operated so as to tum the disk 172 cou-nterclockwise, 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 1% is lowered and depresses the left end of the lever 184. When the lost motion in the link 186 has lbeen taken up, the spool 188 is lowered. This permits pressure uid 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 4hydraulic pressure fluid to flow through the conduits 64 and 71 to the upper end of the servo 72 and rotates the A shaft counterclo-ckwise. The depression of the spool 62 in turn 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 needle 57 to the left, thus reducing hydraulic flow, 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 orifice is reduced, the A `and B shaft motions follow yalong and through the governor feedback mechanism, particularly the link :137 as Well as the connector 101, produces a compensating cotuiterclockwise rotation of the lgear Wheel 1% and a repositioning of the lever 176 by lowering the left end thereof. Also there results a rotation of the quadrant 13d and a repositioning of the lever 184 and the spool 12S. Thus, when the maximum orifice opening or load limit is reduced, the needle is correspondingly moved toward `closed position `and when it has attained the newly set more nearly closed position the parts are again in equilibrium. Substantially the reverse sequence 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 ldisk 192 having an indicator 193 usually graduated in percentage of nominal speed, the indicator illustrating one hundred percent nominal speed in FGURE lA. On the disk 192 there is provided la pin 194 connected by a connector 1% Ito a lever i197 on a shaft 19S. Also on the Shaft is a lever 199 connected by a link 2131 to a lever 262, at its right end pivo-ted 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 rotates the shaft 198 Icounterclockwise also and pulls the link 211 down. Assuming the left end of the lever 262 is `a xed pivot, the right end of the lever 2192 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 h-as 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 also raises the piston of the servo 72 and rotates the A shaft 76 clockwise with governor feedback through the link 101. The rising piston d1 `also -revolves the B shaft 44 quickly in a counterclockwise direction and lowers the sleeve 19, thus admitting pressure fluid to the conduit 161 and opening the orifice 5S with B shaft lgovernor feedback through the link 137. A new posi-tion for the valve cage 122 is thus provided. The speed can be reduced simply yby reverse rotation of the control knob 19.1. 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 decreased in speed under increasing load is referred to as speed droop. Under some conditi-ons, the speed is made to increase under Iadded load and this is referred to as negative speed droop. With the mechanism as shown in the position of FIGURE lA and as so far described, there is no speed droop possi-ble 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 xdisk 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 215 fast on a shaft 216. A fork lever 217 on the shaft 216 is moved counterclockwise and by engagement `with Ia rod 218 translates a roller 219 on the rod to the right o-n an inclined ramp 221.

The ramp is located at a position tangent to ya circle of the diameter of and concentric with the rotational center of a lever 222 on which it is mounted. The lever is supported in a location *between the ends of the ramp 221 and by suitable pivot connections is interposed between the links lll7 and lill. rEhe roller 29 is translated along the Aramp by swinging of the forked lever 2l?. One of the various positions ot 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 2id Awhich carries the roller 2l9 also is connected to a link 223 joined to the lever 262.

When the lever 2id is rotated counterolockwise, the fork lever 217 is 4likewise rotated counterclockwise and the roller Zl 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 M7 and lll@ is effective to displace the link 223. When the roller 23.9 is concentric with lthe lever 222, motion of the links lll7 and M58 does not atleet the link 223 so that the lever 262 in eect has -a fixed pivot at its left end and under these circumstances, there is no speed droop. However, when the roller 219 is disp-laced on the ramp, say to the right, then when there is motion of the links 197 and 108 -a corresponding rotation of the lever 222 occurs and motion is ygiven to lthe link 223. This produces motion of the lever 292 and also or the lever 121, thus readjusting the valve cage 122 correspondingly and permitting the needle 57 -to close somewhat more than it would under a no-droop regulation. A ydisplacernent of the roller oil center to the left similarly `atlords negative speed droop.

The governor controlling mechanism of the invention, although satisfactorily usable with only one nozzle and jet combination, is particularly adapted for and is especially luseful in connection with 'an impulse turbine or other prime mover having `more than one nozzle and needle control. For that reason, the system incorporates an additional nozzle controller representative of any number of individual controllers ol a similar sort. Mounted on the A shaft 76 is a ca-rn 2.3i somewhat similar in shape to the carn 91 but having a sufficiently different 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 of a secondary needle relay valve 234i. The valve 234 is indentical interiorly with the valve i7 and is connected iby a conduit 23e to the pipe 13. Within the housing of the valve 234 there is 4an inlet passage 237 controlled by the spool 233 to allow pressure huid to flow either to a closing conduit 238 or to an opening conduit 239. Suitable restricted outlets 241i and 242 serve to control the rate of operation of -a piston 243 contained in 'a secondary need-le motor cylinder 244i. The piston 243 is provided with a secondary needle 246 etlective by its position to control the rate of flow through a secondary orilice or nozzle 247. The jet issuing from the nozzle 247 impinges upon the same turbine kas does the jet from the primary jet orifice 58.

ln a fashion comparable to that utilized in `connection -with the primary valve 47, the B shaft ldis provided with a lever 251 effective upon rotation of the B shaft to produce a corresponding motion olf a valve sleeve 252 encompassing the spool 233 and assisting in the control of iluid flow through the valve housing 234%. A -spring 253 is interposed between the spool 233 and the sleeve 252 so that they rnove appropriately relative to each other.

There is a valve feedback structure responsive to the movement or the secondary needle 246. This includes a cable 255 extending from the needle to an arcuate lever 257 provided with -an appropriate fulcrum 25S. At its opposite `extremity the lever 257 is connected by a link 259 to the right-hand end of `the lever 232. The eilect of the lever structure 251 is to cause motion of the sleeve 252 immediately upon operation of the B shaft The sleeve motion is followed by an appropriate', more deliberate motion of the spool 233 in response to the slower motion of the cam 231 on the A shaft 76. These motions of both the sleeve and the spool are compensated for by the feedback motion from the secondary needle 2do which causes corresponding motion of the lever 232.

By appropriately positioning the cams 9d and 213i on the A shaft 76 and by appropriately contocring the cams, and further by appropriately adjusting the various discharge restricting devices, such as lo?. and 163 as weil as .1f-lll and 242, the sequential or relative operation of the two needles: 57 and 2li-6 ca-n be precisely controlled. By programming the operation of these two needles and of any others provided with comparable controlling mechanism, it is possible to operate a multi-jet turbine at a substantial improvement in eiiiciency 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 or 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 shalt rl`his is a sudden removal of all load. The nozzle needles because of hydraulic flow requirements cannot be permitted to respond quickly enough to shut down the hydraulic turbine, and hence other means are provided for avoiding excessive over-speed and consequent damage. For that reason, each of the nozzles, such as 53 and 2li-7, is provided with its own dellector, such as 26d md 262, having pivot mountings 26B. As so mounted, the dellectors 2in1 and 262 are normally positioned just outside of the water jets issuing from the nozzles 5% 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 two (or more) detlectors 26d and 262 are connected together by a mechanical connection 25d so that they always move in unison. While the dellector moving mechanism can be mechanically duplicated for each jet, it is usually economically advantageous to provide all of. the deflectors with one actuator serving to operate all of them in unison.

A suit-able actuator includes a piston 266 operating within a motor cylinder 267 and connected by a piston rod 25S to the connection .254 for moving the dedectors. Appropriate motion is given to the piston 266 by hydraulic means. A branch conduit 2&9' `from the pipe 1S joins a dellector control relay valve 27@ at an appropriate port 273i leading into a valve spool chamber 272. Flow through the chamber 272 is controlled by a valve spool 273 on a stern .274 extending upwardly out of the housing of the valve 27d.

When the valve spool 273 is in the position shown in FIGURE 1B, there is no flow to the motor cylinder `257. When the valve spool 273 is lowered, there is pressure fluid llow through the chamber 2172 into a hydraulic conduit 276 leading into the right-hand end ol the motor cylinder 267, and effective to move the deflectors 261 and 262 into intercept-ing position. Return llow 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 lB, thus withdrawing the dellectors from an intercepting position. Under these circumstances, the return fluid from the right end of the motor cylinder 267 flows back through the conduit 27d and out of the valve housing 27d to the reservoir or sump. The valve spool 273 is under the control of a servo mechanism 273 `operated by hydraulic llud conducted to the valve housing 27d through a conduit 279 extending from the 9 filter 19 and controlled by a translatable Valve spo-ol 230 and a valve sleeve 281. The spool and the sleeve are appropriately urged relative to eac-h other by an inter- K posed :spring 282.

Motion orf the spool 289 is derived primarily from the A shaft 76 and the B shaft 44. rthe A :shaft 76 at one end carries a suitably contoured cam 2&6 acting against a follower 287 connected to one end of a fioating 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 2%. A hanging link 293 depending from the link 288 is connected at the other end to a lever 294i between its ends joined t-o 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 iiuid to ow through the conduit 318i to depress the piston d1 quickly and to rotate the B shaft 44 a substantial amount in a clockwise direction. This drops the llink 293 and depresses the left end of the lever 21% to lower the valve spool 280. Pressure fluid from the conduit 279' is tl us permitted to ow immediately into the upper end of the servo mechanism 278 and to lower the valve spool 273. Then, pressure iluid from the conduit 269 flows into the conduit 276 and immediately drives the piston 266 to the left in FIGURE 1B, promptly interposing the deectors into the `several hydraulic jets.

The downward motion of the piston 41 which rotates` the B shaft 44 initially, by its Vservo action, also causes lowering lof the piston '73 but at a relatively slow rate. This lowering rotates the A shaft 7 6 in a counterolockwise direction following the rotation of the B shaft 44.1. -Rotation of the A shaft 76 rotates the cam 236 in a counterclockwise direction, lifts the left end of the link 288, lifts the hanging link 293 and lifts the valve spool 23u from its previously lowered position. This permits liu-id to ilow into the servo 275 to lift the stem 274 and so lifts the valve spool 273. The piston 266 is moved to the right and pulls the deectors 261 and 262 away `from the jets. The movement of the valve spool 273 under the action of the servo 278 correspondingly moves a lever Stil bearing upon the valve sleeve 281 and'forming part of a servo feedback so that the sleeve 281 follows the motion of the stem 274iand tends to stop the action which the initial movement of the spool 28d` has started. During normal operation, the [foregoing structure moves the deiiectors to follow just outside the varying jets and acts to hold them out during proper operation. But when gross over-speed occurs, the B shaft 44 lowers the valve spool 23d and through the servo 278 shifts the valve spool 273 to move the piston 266 to the left, thus interposing the deiiectors 261 and 262 in the jets. The deflectors are always in position so that they can be very quickly interposed lin the jets yet under normal operations do not in any wise interfere with the eliiux of the water.

A feedback mechanism is provided for the deliectors. Connected to the piston rod .263 is a cable 302 extending to an arcuate lever 393 having a suitable fulcrum 36d and connected by a link 306 to a rocking lever 367. This lever, having a fulcrum 368, is connected to the plunger 34?@ of a dash pot mechanism 311 quite comparable to the dash pot mechanism 112. The plunger 3%9 operates to displace hydraulic `liquid between a lower chamber 312 and an upper chamber 313, the displacement rate being controlled iby la needle regulator 3&4. EX- cesive hydraulic liquid in either of the chambers is clicctive correspondingly to displace a spring centered piston 3116 connected to the right end of the lever 294.

if the deflectors 261 and 262 move at an excessive or at a dicient rate as established by the regulator 314, there is a momentary excess of hydraulic duid in one 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 23?. There is consequently provided with this mechanism a controller responsive to the governor primarily, and effective to interpose dcectors in the various jets in accordance with a controlled program.

While automatic oper-ation 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 flow to an outlet conduit 324 extending to a chamber 325 in the bottom of the isolating valve 2d. 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 ill-ustrated so that there is no active flow through the housing 24.

A conduit 32S extends from the transfer valve housing 322 and is connected to a port 329 in the blocking valve housing 28. Pressure 4from the conduit 328 is eifective to depress a piston 3311 in the housing 2S against 'the urgency of a spring 332 so that the valve stem 333 on which the piston 331 is situated is normally held in its open and free-dow 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 354 extending to the reservoir or sump. When this occurs, the press-ure drops and the spring 327 immediately lowers the valve spool 326, thus opening all of the ports in the isolating Valve housing 24. At the same time, the drop in pressure Within the top of the chamber in which the piston 331 operates is sucient so that the spring 332 lifts the valve stem 333, thus blocking flow through all of the ports in the blocking valve housing 28. Furthermore, the valve stem 333 in lifting abuts an adjustable arm 336 on the B shaft 43d and rotates the B shaft counterclock-wise or holds the B shaft in a selected position. This holds the primary needle relay valve 47 with its sleeve or cage 49 in a liXed position and also holds the sleeve or cage 252 of the secondary needle relay valve 234- in fixed position.

With this position of the mechanisms 24 and 2S, the main control is by hand manipulation of the hand regulator 171. This causes motion of the lever 176 and of the link .17S to revolve the shaft 181 correspondingly. A lever 341 on the shaft `131 moves a valve core 342 Within the housing 24 and against a spring 343. Motion of the core 342 controls flow from the pipe 23 into either of the pipes 68 or d1. Return flow from either of those pipes is diverted byV the core 342 into a discharge line 34d leading back to the hydraulic sump. The pipes 68 and 81, being joined to the conduits 71 and 77, respectively, operate the piston 73 and rotate the A shaft 76 to move the valve spools 93 and 233 and so move the needles 57 and 246. Any needle position can thus be manually attained with the aid of the hydraulic system and the A shaft.

Sometimes hydraulic pressure for operation is available only by hand pump (not shown). Then much of the hydraulic mechanism is not used. Rat ler, :a clutch 346 0n the A shaft 76 is shifted to the right (FIGURE 1A) and disengages the rest of the shaft from the crank 74. A handle 347 serves for the manual and direct rotation of the shaft 76 connected thereto and the direct positioning of the valve spools 93 and 233. A hand pump supplies temporary hydr-aulic pressure to move the piston S6 and needle 57 and the piston 243 and needle 246. The clutch 346 is re-engaged iwhen manual hydraulic or automatic hydraulic operation is to be resumed.

ll With the mechanism described herein it is possible to secure good speed and load response and regulation with a plurality of jets and deiiect rs. Upon the occurrence of overspeed, lfor example, the B shaft moves accordingly and almost instantly. This response is at a predetermined rate although the range or amount o B shaft movement is not great since the ilyballs -li make only small excursions from steady state position in order to assure close regulation. Consequently, the sleeves, such as 9, move promptly at a predetermined rate but only through relatively short distances. The B shaft motion, even though slight, by reason of valve spool 62 in the control relay mechanism 32. initiates a corresponding but slower motion of the A shaft. The longer the il shaft is out of steady state position, the farther the A shaft moves from its own steady state position and the more the spools, such as 93, are moved to afford an appropriate compensation.

What is claimed is: l. A governor control for a water Wheel having a lirst nozzle needle and a second nozzle needle comprising a rst means vfor positioning said iii'st needle,

said iirst means including a irst hydraulic actuator ad a iirst hydraulic valve having a ii-rst spool and a rst sleeve for controlling hydraulic flow through said iirSt valve to said rst hydraulic actuator, a second means vfor positioning said second needle,

said second means including a second hydraulic actuator and a second hydraulic valve having a second spool and a second -sleeve for controlling hydraulic liow through said second valve to said second hydraulic actuator, means responsive to water wheel speed for simultaneously moving both said iirst sleeve and said second sleeve at the same predetermined rate, and means controlled by the movement of said responsive means for simultaneously moving both said first spool and said second spool at mutually dilierent rates. 2. A governor control for a Water wheel having a nozzle needle comprising a hydraulic motor for actuating said needle, a hydraulic circuit connected to said hydraulic motor, a valve in said hydraulic circuit, said valve having a movable spool and a movable sleeve in series for controlling hydraulic ilow through said valve, means responsive to water wheel speed, means actuated by `said speed respons-ive means for moving said sleeve at a predetermined rate, and means controlled by the movement of said .actuated means and independent of said hydraulic motor for moving said spool at a different rate. 3. A governor' control for a rotary prime mover comprising means movable into different positions to control the rotational speed of said prime mover, a hydraulic motor for positioning said movable means, a hydraulic circuit connected to said hydraulic motor, a valve in said hydraulic circuit including a rst member and a second member in series for controlling liow in said hydraulic circuit, means responsive to prime mover rotational speed, means moving under control oi said speed responsive means for operating said first member at a predetermined rate, and means controlled by said moving means independently 'l2 of the position of said hydraulic motor for operating said second member at a ditlerent rate. 4. A governor control -for a rotary prime mover compricing first means movable into dilerent positions to control prime mover rotational speed, first hydraulic means for moving said first means, a lirst hydraulic circuit for said lirst hydraulic means, a lirst valve in said lirst hydraulic circuit including a spool and a sleeve in series for controlling :dow in said rst hydraulic circuit, second means movable into diilerent positions to control prime mover rotational speed, second hydraulic means `for moving said second means, a second hydraulic circuit for said second hydraulic means, a second valve in said second hydraulic circuit including a spool and a sleeve in series for controlling lflow in said second hydraulic circuit, responsive to prime mover rotational spee means moving under control of said speed responsive means for operating both of said sleeves in unison at a predetermined rate, and means controlled by said moving leans independently oi the posit-ion of said tirst means and said second means `lor operating both of said spools in unison at mutually different rates. 5. A governor control for a prime mover comprising means movable into diilerent positions to control the speed of said prime mover, power means `for moving said movable means, .a pouver circuit for said power means, a first member and a second member in series for controlling the flow of power in said power circuit, means responsive to prime mover speed, and means controlled by said speed respon-sive means for operating said first member and said second member at mutually different rates and independently of the position of said power means Afor a given response of said responsive means. 6. A `governor control for a Water Wheel having a 'lirst nozzle needle and a second nozzle needle comprising first hydraulic moving means for moving said first .eedle, second hydraulic moving means for moving said second needle, a lfirst valve having a first spool and a first sleeve for operating said first hydraulic moving means, a second valve having a second spool and a second sleeve for operating said second hydraulic moving means, a lirst feedback mechanism from said first hydraulic moving means to said lirst valve, a second feedback mechanism from said second hydraulic moving means to said second valve, means responsive to water Wheel speed, irst :means controlled by said speed responsive means for operating said first valve sleeve and said second valve sleeve simultaneously, `second means controlled by said lirst means for operating said iirst valve spool and said second valve spool, and means for controlling the speed of operation of said second means. 7. A device as in claim 6 in which said second means includes a first cam engaging said rst valve spool, and

a second cam of different shape than said first cam engaging said second valve spool.

References Cited in the le of this patent UNITED STATES PATENTS 5 1,234,882 Doble July 31, 1917 1,613,950 Jackson Jan. 11, 1927 14 Deglon May 16, 1939 Rued Apr. 21, 1953 Wheeler et lal. May 10, 1955 Wheeler Oct. 28, 1958 Avery Aug. 11, 1959 FOREIGN PATENTS Great Britain Aug. 9, 1923

Claims (1)

1. 5. A GOVERNOR CONTROL FOR A PRIME MOVER COMPRISING MEANS MOVABLE INTO DIFFERENT POSITIONS TO CONTROL THE SPEED OF SAID PRIME MOVER, POWER MEANS FOR MOVING SAID MOVABLE MEANS, A POWER CIRCUIT FOR SAID POWER MEANS, A FIRST MEMBER AND A SECOND MEMBER IN SERIES FOR CONTROLLING THE FLOW OF POWER IN SAID POWER CIRCUIT, MEANS RESPONSIVE TO PRIME MOVER SPEED, AND MEANS CONTROLLED BY SAID SPEED RESPONSIVE MEANS FOR OPERATING SAID FIRST MEMBER AND SAID SECOND MEM-

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