US2571842A - Governor mechanism - Google Patents

Description

Oct. 16, 1951 J, 3 DALE 2,571,842

GOVERNOR MECHANISM Filed March 18, 1946 4 Sheets-Sheet l 6/ .93 i 36 66 C 7 I 84 d 'ZJJ 2:; i j 5 X 9 za i Oct. 16, 1951 J. s. DALE 2,571,842

.GOVERNOR MECHANISM Filed March 18, 1946 4 Sheets-Sheet 3 Oct. 16, 1951 J. s. DALE 2,571,342

GOVERNOR MECHANISM Filed March 18, 1946 4 Sheets-Sheet 4 Patented Oct. 16, 1951 UNITED STATES PATENT OFFICE GOVERNOR MECHANISM Joseph S. Dale, Rockford, Ill. Application March 18, 1946, Serial No. 655,086

4' Claims.

This invention relates to governor mechanism and is particularly applicable to governors of the hydraulic type.

.An object of the invention is to provide a governor of simple construction, capable of responding more quickly to speed changes and correcting such changes more rapidly than governors heretofore employed. A further object is to provide a governor structure in which improved control means are provided, regulating more accurately the flow of pressure fluid to the servomotor. Yet another object is to provide a novel fluid control valve mechanism in which the force resulting from dynamic unbalance is reduced to a minimum and is not transmitted to the speeder spring and fly weights. Another object is to provide a governor structure in which novel speed adjustment mechanisms and speed droop adjustment devices are provided. Yet another object is to provide a spring drive mechanism whereby effective rotation of the fly weights is accomplished; while at the same time absorbing slight oscillations of the prime mover. Other specific objects and advantages will appear as the specification proceeds.

The invention is illustrated, in preferred embodiments, by the accompanying drawings, in which Figure ,1 is a perspective view of governor mechanism embodying my invention; Figs. 2 and.2',

vertical sectional views, the section being taken as indicated at line 2-2 of Fig. 1 but showing two different constructions; Figs. 3, 3' and 3", transverse sectional views, the sections being taken as indicated at line 3-3 of Fig. 2' but showing three different constructions; Fig. 4, a transverse sectional view, the section being taken as indicated at line 44 of Fig. 2'; Fig. 5, a broken view similar to Fig. 2' but showing a modified form of the invention; Fig. 6, a perspective view of'the main drive shaft or ball head drive shaft employed; Fig. 7, a perspective view of a modified form of the valve sleeve employed; Fig. 8, a broken sectional view of'a drive shaft equipped with a spring drive member; and Fig. 9, a transverse sectional view, the section being taken as indicated at line 9'9 of Fig. 8. Similar reference numerals are applied to corresponding parts throughout the views. For example, corresponding parts in Fig. 2 are given prime numerals to show relationship to corresponding parts in changes of the prime mover; and C, adjustment means for controlling the load on the speeder spring under various operating conditions.

The casing A may be of any suitable construction. In the particular illustration given, I0 designates a base plate, II, a block or frame structure carried by the plate liLand I2, a dome structure resting upon the body member I I. The dome member I2 is provided with a flange base I3 through which screws I 4, Fig. 2', extend to secure the dome in place on the block II, other screws M, Fig. 2', beingprovided to fasten the base plate It to the block II. A gasket I5 may be provided between the flange structure It and the block II. Another gasket [5 is provided between the base plate l0 and the block II.

The block II may be formed of a solid piece of metal, or a cored casting, having openings therethrough providinga pump chamber, shaft openings, and conduits for the supply of fluids, etc.

The dome casing I2 is provided at its top with a shoulder II. A recess I6 is provided under the cap 9' (Fig.2), or the cap 9 (Fig. 2). In the construction shown in Fig. 2, the cap 9' is held to the dome l2 by cap screws. In the construction shown in Fig. 2, the cap 9 is threadedly engaged to the dome I2. The casing I2 provides in its interior a chamber adapted to receive the fly weight mechanism, etc.

The control mechanism B may be of any suitable type or structure. In the illustration given, I provide a ball head I8, equipped with a reduced extension I9. In Fig. 2, a collar 2| is pressed on extension I9 and bears against shoulder II to retain the ball head IS in place. In Fig. 2', the extension. I9 is tapped to receive a threaded bolt 20. The bolt20 carries a flange 2| which rests upon the shoulder I'I, thus holding the ball head I8 in place. The fly weights 22 are secured to theball head I8 by the pivot pins 23 and are free toswing inwardly or outwardly about pins 23. Each of the fly weights 22 is provided with an integral arm 24 extending inwardly and equipped with a toe 25 turned downwardly. The ball head I8 is provided with an integral key 26 for securing the ball head I8 to the ball head drive shaft 21.

The main drive shaft 21, which may also be referred to as the ball head drive shaft, extends vertically through the casing members III and II into the dome l2, and is provided at its lower end witha slot 28 suitable for connecting it to the driven part of the prime mover. Shaft 21, therefore, rotates in synchronism with the driven part of the prime mover. "Shaft 21 rotates in bore 33 and is provided near its lower end with an integral gear member 29 which serves as a part of the gear pump which will be later described. Above the gear 29, the block ll is provided with outlet ports 30 leading to the sump of the prime mover or any other desired collection point for the pressure fluid, through chamber 30 and passage 38*. Above the ports 30 on the shaft 21 are two spaced lands 3| and 32 which, when enclosed by a. sleeve 40, as will be later described, provide between them a chamber 5! for the pressure fluid. Covered by the land 3|. are a series of control ports 41 in the sleeve 40 which are effective in controlling the flow of fluid to and from the servomotor. Shaft 21 is provided with a slot 34 which receives the key of the ball head l8 and thus establishes a connection for the rotation of the ball head 18 by means of the shaft 21.

Supported within the chamber of the dome l2 and between the fly weights 22 is an inverted frust'oeconical speeder spring 35. The lower end of the spring rests upon a Speeder spring seat 36. The upper part of the spring supports a cup member 31 which provides a shoulder 38 at its lower end. Resting upon the shoulder 38 is the flange 39 0f the pilot valve sleeve 40. Above the sleeve 4ll isa-ballthrust bearing 4|, the lower race of which rests upon the flange 39 and the upper race of which engages the toes 25 of the fly ball arms 24. The speeder spring seat 36 is preferably equipped with an integral, upwardlyextending sleeve 42 which serves to guide the seat 36. Preferably, the sleeve 42 extends also slightly belowthe seat 36; The spring seat 36 and sleeve 42 receive and are guided by a bush- 4 ing 43 which is pressed into-thebore'33' provided in block II, this bushing 43 being one of three (43 and 43) pressed into the bore 33- in spaced relation to one another-to provide annular chambers 45 and 48 around the sleeve in the vicinity of ports-44- and 47.

The pilot valve sleeve 40 is preferably formed of thin metal so that it will be light and may be moved easily longitudinally of the shaft 2T to provide an accurate control of the flow of the pressure fluid. It is suspended from the upper spring seat 31 by means of itsflange 39' resting on the shoulder 38 and'moves downwardly in response to pressure exerted upon the ball thrust bearing 41 by the toes- 25 of the fiy'ballarms 24. The sleeve 40 is provided with inlet ports 44 and the control ports 41 previously mentioned. The inlet ports 44 register with the chamber 45 fed by the fluid conduit 46. The outlet; or' control', ports 41" register with the annular chamber 48 which communicates with a conduit 49 leading to the servomotor chamber 50 (Fig. 4) The ports 4"! cooperate with the land 3! of shaft 21 in controlling the flow of fluid from the annular chamber 5| provided. between lands 3|. and 32 and into the servomotor conduit 49.

For supplying fluid under pressure for the operation of the servomotor, I provide a gear pump which consists of gear 29 on shaft 2T, and'an idler gear 52' meshing with gear 29, as shown in Fig. 2. The gears29 and 52,,as shown in Fig. 2', are mounted in recesses provided in the lower portion of casing block |.l.. Fluid. issupplied to the pump by any suitable means- Three forms of relief valves are shown in Figs. 3, 3 and 3".

In Fig. 3, the block H, or II as the case may be, is provided with a reamed diameter hole. H and a reamed diameter hole 51. A ball. 62, spring loaded, as at 64', and held against seat 63, acts as a relief valve. Lubricating oil is admitted to the governor from the prime mover lubricating pump through channel 56 in fitting 53. This fluid goes through channel 59 to the suction side of the gear pump formed by the gears 29 and 52. This fluid under pressure goes to channel 60. The spring 64 determines the maximum fluid pressure. If pressure is sufficient, the ball 62 is lifted off of the seat 63, allowing the fluid to flow past the ball 62 to the channel 29 as the suction side'of'the gear pump.

Fig. 3 illustrates a second method using a plunger 62 instead of the ball 62.

Fig. 3 illustrates a third method. In the illustration given, the block H is provided with a tapped opening receiving the fitting 53, as shown in. Fig. 3". The fitting 53 is provided with a threaded opening 54 adapted to receive a pipe 55, as shown in Fig. 1, said pipe leading to any suitable source of supply, as, for example, the lubricant pump of the prime mover. Incoming fluid passes through the opening 56 of the fitting 53 and into the spring chamber 51* provided in the fitting 53 A port 58 permits: the liquid to flow into the inlet conduit 59, leading to the inlet sideof the gear pump The gear pump forces the liquid under pressurethrough conduit Bil into the passage 61', which is normally closed by the plunger 62 The plunger 62 is urged toward stop pin 63 by the spring 64. When the pressure of the fluid overcomes the'pressure of spring 54, the plunger t2 moves, compressing the spring, and uncovers port 65. Fluid is thus-permitted to escape through relief'port 65 and to return to the inlet side of the gear pump. By the means described, a predetermined pressure is maintained within the outlet passage of the pump, while at the same time a relief is furnished against excessive pressures. The conduit 46 leads off from the passage 61' to supply fluid to the chamber 51 about shaft 2-1.

It should be obvious that in the event of a reverse direction of drive for shaft 21; the gearpump, being driven in the opposite direction, makes the passage 60 the inlet and passage- 59 theoutlet, and in such event the plug 53 will be entered in hole153, plug 53 being'interchanged with plug 53*.

The adjustment mechanism varyingthe elevation of the speeder' spring seat'36 maybe of any suitableconstruction. Three methods are illustrated in Figs. 2,2 and Fig. 5.

In' the illustration in Fig. 2; I provide an arm 89 which bears intermediate its end's underv the. spring seat 36', the plunger 83" through the ball. B4, and. the cam. El which is fastened by screws to the cutaway section of the speed-adjusting shaft 12'. The speed-adjusting shaft I2 through the cam. 3|. raises or lowers the spring seat 35 thus changing thespeed Setting. of the governor. With. a fixed setting of shaft 12', as: the load on the prime mover increases. the servomotormoves outwardly and the cam 18., due: to the setting: made by the screw 84-, allowstheplunger 83" to. move. downwardly. This lowers the ball 88 and the point of contact between arm 89 and the spring seat 36', thusgivinga lower speed setting. as. the servomotor 19' moves outwardly. Thus, we have speed droop and a stable operating; governor. This is the speed droop adjustment. more fully described hereafter by reference to. Figs. 2- and4.

The construction shown in Fig.5 is thesame as illustratedin- Fig. 2: except that the arm Ba is pinned to the plunger 83? by the pin 68.

In.the illustration in Fig. 2", I provide a fork member 66, having its forked end portion extending around the sleeve 42 and engaging the flange seat 36, as illustrated in Fig. 2'. The rear portion of the fork 66 is provided with a boss 61 which is secured by pin 66 to a block member 69. The block member 69 is also pivotally mounted upon pin I which secures it to the block II In order to raise or lower the fork 66 and thereby the springseat 36, I provide a rotatable cam member II which has a cylindrical shaft portion I2 extending outside of the block II, a illustrated in Fig. l, and provided with a slot I3 by means of which the shaft I2 may be rotated. The inner cam portion II may be shaped as illustrated in Fig. 2 and the rotation thereof will elevate fork 66 and thereby the spring seat 36.

I provide special means herein for automatically taking care of speed droop. Speed droop, which is a decrease in governor speed setting as the servo is opened, is used for stabilization. Mountedwithin the servomotor chamber 50 of easing I I is the servo plunger I4, as illustrated in Fig. 4. The plunger I4 is provided with a forked outer end I5 for connection to a control rod (not shown) connected to a fuel pump. gas mixing valve, steam throttle or other device for controlling the supply of fuel or other energy medium to the prime mover. The plunger- 16 is provided on its lower side with a keyway I6 in which a key 11 extends, the key being pressed in a hole provided therefor in block II, as illustrated in Fig. l. A cam member I8 is mounted for pivotal movement upwardly and downwardly upon pin 19 carried on the inner end of plunger I4 and said cam I8, and is adapted to engage the flattened ball-8ll. The elevation of the cam member I8 is controlled by a threaded pin 8|, having an inwardly-extend ing point engaging the cam and an outwardlyslotted portion 82 adapted to be engaged by a screw driver for inward or outward adjustment of pin8l. i

The correcting influence of cam I8,;in connection with speed droop, is transmitted through the flattened ball 86 and other mechanism in order to adjust the speeder spring seat 36. In this mechanism, a plunger 83 is provided with a rounded seat receiving the upper portion of ball 80 and with another rounded seat receiving the lower portion of upper ball 84. The upper ball 84 bears against block 69 at a point inwardly from the pivot pin 10, as illustrated in Fig. 2'. Above the block is mounted a leaf spring 34 which maintains a constant downward pressure upon block 69, ball B4, and plunger 83, and thus through ball 86 exerts a downward force on cam I8. An upward thrust by the cam 18 during the movement of the servomotor will cause the ball members 86 and 84, through the plunger 83, to elevate the fork member 66 at a point inwardly from the pivot pin I0, and thus will tilt downwardly the inner end of fork 66 so as to lower the speeder spring seat 36. Likewise, cam I8 may permit a lowering of these members which will produce a corresponding rise of the speeder spring seat 36.

"Shaft 27 is undercut between lands 32and I I9, thus forming a chamber I01. A cross-hole I06 is drilled in shaft 21, and a longitudinal hole I68 of larger diameter than the width of the key 26 is also drilled in shaft 21. Pressure oil will leak over land 32 into chamber I01. This oil will be forced through holes I06 and I08 into chamber I6, where it serves as a lubricant for the ball head, this oil eventually finding its Way to chamber 3|] communicating with the sump of the prime mover.

Operation In the operation of the governor, as shown in Figs. 2 and 3, the pressure fluid enters the block II, through the passage 56 in fitting 53, as shown in Fig. 3, through chamber 51' to the inlet conduit 59 to the gear pump, which will force the fluid through conduit '60 and upwardly into chamber 51 and conduit 6|. If the pressure here becomes excessive, the ball 62 is forced off the seat 63, against the spring 64, thus allowing the fluid to flow past the ball 62 into the chamber 51 to the inlet conduit 59 of the gear pump. By this means described, the fluid within the conduit 6| is maintained at the desired pressure and provides a supply of fluid under pressure to the conduit 46 leading to the chamber 5 I' provided between the shaft 21 and the pilot valve sleeve 40'. V

In the operation of the governor, as shown in Figs. 2 and 3', the pressure fluid entersthe block I I, through the passage'56 in fitting 53, as shown in Fig. 3, through chamber 51f to the inlet con duit 59 to the gear pump, which will force the fluid through conduit 60 and upwardly into chamber 51 and conduit 6|. If the pressure here becomes excessive, the plunger 62 is forced off the seat 63, against the spring 64, thus allowing the fluid to flow past the plunger 62 into the chamber 57, to the inlet conduit 59 of the gear pump. By this means described, the fluid within the conduit 6| is maintained at the desired pressure and provides a supply of fluid under pressure to the conduit 46 leading to the chamber 5| provided between the shaft 21' and the pilot valve sleeve 40'. V

In the operation of the governor, as shown in Figs. 2' and 3", the pressure fluid enters the block II through passage 56 and port 58, as shown in Fig. 3", to the inlet conduit 59 of the gear pump, which will force the fluid through outlet conduit 60 and upwardly into conduit 6|. If pressure here becomes excessive, plunger 62 is moved suiflciently to uncover port 65, thus allowing the return of pressure fluid to the inlet side of the pump. By the means described, the fluid within conduit 6| is maintained at the desired pressure and provides a supply of fluid under pressure for conduit 46 leading to the chamber 5| provided between shaft 21 and pilot valve sleeve 40. I

Shaft 21, which is connected to a driven part of the prime mover, rotates with said driven part and produces a similar rotation of the ball head I8, which is suspended upon bearing |'I-. Upon an increase in speed, the fly weights 22 tend to swing outwardly, and this action causes the arms 24, which are rigid with the fly weights 22, to move downwardly and to press their toes 25 against the upper race of the ball bearing 4|. The downward movement of bearing 4| is resisted by speeder spring 35 and causes a corresponding downward movement of pilot valve sleeve 40. As the pilot valve sleeve 40 moves downwardly under the thrust of the fly weights 22, the lower portions of the ports 41 are opened. The servo piston or plunger I4 is externally spring loaded (not shown) so that the spring tends to move the servo plunger inwardly to fuel-off position. The lower portion of the control ports 41 being opened, allows more oil to flow from the channel or conduit 49 into, the space between the sleeve and shaft 21, and thus to escape through the attract dump ports-30. The-escape of the pressure fluid gives a lower fluid pressure on the" servo piston or plunger 14 and the piston' is, therefore, free to yield to the action of the servo pull-back spring. The inward movement of the servo piston or plunger 14 toward the fuel-off position results in a slowing down of the prime mover.

The operation of the governor is exactly in the reverse direction when the speed of the prime mover, as reflected by the speed of rotation of shaft 21, is decreased. In this action, the reduction in centrifugal force causes the'fly weights 22 to swing inwardly and the" pressure upon'the bearing 4 I is reduced. Speeder spring 35, there fore, raises the shoulder 38 and thereby the pilot valve sleeve 40. Upward movement of the sleeve 40 closes the lower portion of the ports 41, thus cutting off the flow from channel 49 toward the dumpportsSD; while causing the flow of pressure fluid from the chamber 5| into the servo conduit 49. The increase of pressure fluid in the servo chamber 50 causes the servo piston or plunger 14 to move outwardly and to overcome the pressure of the pull-back spring; This movement increases the fuel supplied to the prime mover and thus" the speed of the prime mover increases.

As shown in Fig. 2, the speed setting of the governor is changed by rotating the shaft 12" so that'thecam 9| raises or lowers the arm member 89'. The arm member 8 9 in turn exerts pressure against the'seat 35' to increase or decrease the loading of the speeder spring 35'.

As shown in Fig. 5, the speed setting of the governor is changed by rotating the shaft 12 so that the cam 91- raisesor lowers the arm member 89*. The arm member t9 in turn exerts pressure against the seat 36' to increase or decrease the loading of the speeder spring 35-.

As shown in Fig. 2', the speed setting of the governor is changed by rotating the shaft 12 so that the cam 1i raises or lowers the fork member 66'. The. fork member 66 in turnexertspressure against the seat 36 to increase the loading. of speeder spring 35, or, upon lowering of the fork;.to-reduce the loading of the spring 35-.

Withrespect tospeeddroop, if thespeed of the prime mover and the governor decreases, then the servo piston or plunger 14 moves outwardly; Assillustrated in Fig. 2, this movementcauses the canrTS', whenthe cam is-adjusted to the desired angular position by means of the pin 81", to move theball members 88' and 84' and the plunger 83.. If the members are lowered, they lower the end of the armBS, thus lowering. the spring seat 36 and thus reducing the load on thespeeder spring 35 The opposite or inward movement of the servo. piston or plunger 14' increasestheloading on the speeder spring 35'.

With respect to speed drool if: the speed oi the prime mover andthe governordecreaseathen the servo piston or plunger. 14 movesoutwardly. As illustrated in Fig. 5, this movement. causesthe cam 18,- when the cam isadiusted to the desiredangular position by means of the pin 68. ,to-movethe ball members. as and 84 and the plunger 83. If the members are lowered... they lower the end of the arm 89 ,.thus lowering. the springseat 36' and thus reducing the load on the speeder spring 35'. The opposite or inwardmovement' of the servo piston or plunger increases the loading on the speeder spring With respect to speed d'roop, i'fthe speed of the prime mover and the governor decreases; then the servo piston or plunger 14' moves outwardly. As illustrated in Fig. 2", this movement causes cam 1-8, when the cam is adjusted to thedesired n: on

angular position by means of pin 81 to move the ball members and 84- and plunger 83. If the ball members are raised, they move the outer portion 61 of the fork B6 upwardly so that the inner end of the fork drops downwardly. allows seat 35 to dropand decreases the loading of thespring 35'. The opposite movement allows the spring 34 to move the outer portion 51 ct for-k 66 in a downward direction and thus raises the forked end of member 66 and seat 36, whereby the loading of spring 35- is increased.

The effect of the new structure upon dynamic unbalance should be mentioned. When oil flows over a land and through a port, a force is set up which tends to close the port opening in prior pilot valve structures. This force inprior structure is exerted on the land and is transmitted to the speeder spring and fly balls or weights. In my new structure as above described, the la-nd- IN or 3i, as the case may be, is on the shaft 21 which is held in a fixed vertical position, and this force is therefore not transmitted tothe speeder spring- 35 and fly balls 2-2.

The reduction in thickness of the sleeve 40' minimizes the reaction force transmittedto the fly balls 22 and speeder spring 35'.

Any suitable means for closing theservo chamber 50 may be employed. In the illustration given in Fig. 4, the opening of the servo chamber is closed by a cover 86 secured by four screws 81', or other means, to the block H.

Itwi-ll be understood that the pilot valve sleeve heretofore described may be modified widely. In the illustration given. in Fig. '1, a sleeve 40 is employed, having a flange 39 near the top portion thereof adapted to rest upon the shoulder 38- of the upper spring seat 31. With this structure, the tube is equipped with an extension 94' receiving the shaft 21 and lying within the ball bearing 4|.

One difliculty with governors now in use is that with certain prime movers, oscillations of the prime mover will be transmitted to the governor, causing an uneven operation of the governor that is objectionable. To overcome this difficulty, I

havep'rovi'ded a flexible or'resilient' spring drive which will transmit force from the prime mover to rotate the ball head but will not transmit the slight oscillations referred to. Such movements areabsorbed in the spring connection and, therefore, do not adversely affect the operation. of the governor;

In the structure shown in Figs. 8 and 9, Iprovide a shaft 95 which is substantiallyidentical with shaft 21 except that it is provided with a longitudinal channel 96. I employ a spring wire 91 to connect the lower portion of the shaft 9.5 andan' upper driving head 98.. A hole 99 is drilled into the lower portion of the shaft 95, and the spring wire 91 is made fast Within this hole,.either by a pressed fit, threaded engagement, welding, or other means; Similarly, the upper end of the spring wire 91 is fixed to the shank Hill of the couplerhead 98. The head 98 is provided with a narrow slot HJ'I' which is substantially the same as the slot 34 of shaft 21. The slot 101 opens, however, into a flared slot I92 formed in the upper end portion I03 of the shaft 95, as shown more clearly in Fig. 9. The key 25' on the ball head has one portion Hi4" fitting closely in slot in I and has two" depending. end portions I05 which have a lost motion fit in the flared slots 1'02. With this construction, the head 98 will always drive the ball head It through spring, 91 as long as the spring is effective. Should the spring 97 9 break and no longer be sufficient to carry the load from shaft 95 to head 98, the key 26 of the ball head I8 will engage its lower portions H in the flared slot I92 in the upper end I93 of shaft 95 and thus shaft 95 will directly drive by means of slot I02 the key 26 of ball head l8.

With the modified structure shown in Figs.8 and 9, it will be seen that I have provided a structure which will normally drive the ball head 18 only through the resilient spring 91. By this means, any slight irregularities or oscillations of the prime mover will not be transmitted to the ball head but will be absorbed by the resilient member 9! itself. Should, however, the member 91 break or fail to carry the load, a direct drive is provided by means of the flared slot I02 in the upper end of the shaft 95, which slot will engage the key 26 the moment spring 91 becomes ineffective as a driving connection.

While in the foregoing description I have set forth a great variety of details as illustrating preferred embodiments of my invention, it will be understood that such details may be varied widely by those skilled in the art without departing from the spirit of my invention.

I claim:

1. In a speed governor adapted for use with a hydraulic servomotor to control the speed of a prime mover, control apparatus comprising a shaft adapted to be rotated by the prime mover and having thereon a pair of spaced lands, said shaft being held against axial movement, fly weights mounted on said shaft for rotation thereby, a speeder spring, a slidable valve tube mounted coaxially with the shaft and supported by the speeder spring, said tube being secured against rotation and operative to provide a chamber between said lands, inlet and outlet ports in said valve tube, and means carried by the fly weights for moving said valve tube against the force of said spring operative to vary the relative position of one of the lands and the outlet port and thereby to control the flow of fluid between the chamber and the servomotor.

2. In a speed governor adapted for use with a hydraulic servomotor to control the speed of a prime mover, control apparatus comprising a shaft adapted to be rotated by the prime mover and having thereon a pair of spaced lands, said shaft being held against axial movement, fly

weights rotated by said shaft, a speeder spring supported to oppose movement of the fly weights, an axially-slidable valve tube mounted coaxially with the shaft and providing a fluid chamber between the lands, said tube being suspended from 4 said spring and being provided with inlet and outlet ports, the outlet port being adapted to communicate with the servomotor and to regulate the supply of fluid thereto responsively to relative movement of the valve tube and the shaft.

3. In a speed governor adapted for use with a hydraulic servomotor to control the speed of a prime mover, control apparatus comprising a shaft adapted to be rotated by the prime mover and having thereon a pair of spaced lands, said shaft being held against axial movement, fly weights rotated by said shaft, a speeder spring supported to oppose movement of the fly weights, a thin, light valve sleeve mounted coaxially with said shaft and axially slidable thereon, said sleeve forming a fluid chamber between the lands and being supported by the speeder spring, means carried by the fly weights for moving said sleeve against the force of said speeder spring, and inlet and outlet ports in said valve sleeve, the outlet port being adapted to communicate with the servomotor and to regulate the supply of fluid thereto responsively to relative movement of the valve sleeve and the shaft.

4. In a speed governor adapted for use with a hydraulic servomotor to control the speed of a prime mover, control apparatus comprising a shaft adapted to be rotated by the prime mover and having thereon a pair of spaced lands, said shaft being held against axial movement, fly weights mounted for rotation by said shaft, a speeder spring, a valve sleeve in engagement with the speeder spring and mounted coaxially with the shaft and slidable thereon, said sleeve being operative to provide a chamber between said lands, an outlet port in said valve sleeve, and means for moving said valve sleeve axially 7 against the force of said speeder spring responsively to movement of said fly weights, said axial movement of the sleeve being operative to vary the relative position of the outlet port and one of the lands.

JOSEPH S. DALE.

REFERENCES CITED The following references are of record in the file of this patent:

UNITED STATES PATENTS Number Name Date 1,180,583 Gagg Apr. 25, 1916 1,600,542 Gagg Sept. 21, 1926 2,142,172 Brill Jan. 3, 1939 2,229,681 Sorensen Jan. 28, 1941 2,252,838 Drake Aug. 19, 1941 2,268,230 Warner Dec. 30, 1941 2,270,306 Kalin Jan. 20, 1942 2,292,194 Blymyer Aug. 4, 1942 1 2,294,469 Loeffler Sept. 1, 1942 2,364,115 Whitehead Dec. 5, 1944 2,371,157 Drake Mar. 13, 1945 2,422,966 Hoover June 24, 1947 2,472,050 Staples May 31, 1949

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