US2715892A - Hydraulic governor regulating means - Google Patents

Description

Aug. 23, 1955 A. H. RODECK ET AL 2,715,892

HYDRAULIC GOVERNOR REGULATING MEANS Original Filed Aug. 25, 1948 2 Sheets-Sheet l q 0') w m m 3 INVENTORS Arm/'12 H fiodecfi and A/ber; G. Massgy Aug. 23, 1955 A. H. RODECK ET AL 2,715,892

HYDRAULIC GOVERNOR REGULATING MEANS Original Filed Aug. 25, 1948 2 Sheets-Sheet 2 a Bvenfors 1 259 firm/n H. 'fiodec/a and 25! if] Albert G. Massg United States Patent Ofiice 2,715,892 Patented Aug. 23, 1955 HYDRAULIC GOVERYOR REGULATING MEANS Armin H. Rodeck and Albert G. Massey, Water-town,

N. Y., assignors to Massey Machine Company, Watertown, N. Y.

Original application August 25, 1948, Serial No. 46,098.

Divided and this application November 30, 1953, Serial No. 403,581

7 Claims. (Cl. 12142) This application is a division of our copending application, Serial No. 46,098, filed August 25, 1948, now abandoned.

This invention relates to hydraulic governors for speed control and similar adaptations.

The underlying principles of governor control are adaptable to controlling and regulating various conditions and the principles of the present invention are not limited to any particular field of governor adaptation. However, the widest present field of use of governors is probably in the control of the speed of internal combustion engines and as a convenient way of setting forth the principles of the present invention, reference will be had to such field by way of example. For instance, in Diesel engine installations the governor mechanism is made responsive to changes in the speed of the engine and in response to such speed changes varies the fuel setting of the engine to correct for the speed changes to thus maintain a constant speed or, at least, a predetermined relationship between engine load and speed.

In conventional mechanical flyball governors, the centrifugal flyballs are direct acting and not only indicate speed but also serve directly as as ource of mechanical energy to change engine fuel setting. In such governors a corrective fuel change requires a substantial speed change to overcome friction in the various parts. This results in a tendency to over-govern, whereupon the governor makes an adjustment by a series of over-shooting oscillations in the fuel setting change which gradually damp out at the conclusion of the governing adjustment. This undesirable phenomenon is known as hunting and various expedients and auxiliary mechanisms have been availed of in an endeavor to reduce hunting, and its attendant objections and undesirabilities.

In view of the undesirabilities of direct acting centrifugal governors, particularly from the standpoint of sensitivity, a considerable field of development in hydraulic governors has evolved. In the usual hydraulic governor, relatively small fiayballs are used merely to indicate speed and to move a small pilot valve in a hydraulic system, the valve being arranged to release extraneous hydraulic fluid pressure energy for actually manipulating the fuel control system and other governor adjuncts. The speed change which produces a response in hydraulic governor application can be very much less than in a direct acting centrifugal governor. However, special provision must still be made to eliminate or minimize hunting and conventional hydraulic governors employ complicated hydraulic and mechanical systems to effect compensation, that being the term generally given to the function of reducing hunting to a minimum, so that a new fuel setting due to governor adjustment is attained as nearly as possible by a direct movement from the old to the new setting without objectionable oscillation.

The present invention, in one aspect, has to do with a novel arrangement which results in the substantial elimination of the complicated auxiliary mechanism ordinarily employed in governors to effect compensation and thus eliminate or minimize hunting. The present invention provides means for rendering the governing motive power intermittent or pulsating in character. In the hydraulic governor set forth herein by way of example, the transmission of hydraulic pressure from the pressure source to the power piston during a governing operation is in successive spurts or jets whereby the governing correction consists of a series of intermittent increments of movement on the part of the power piston.

It has been found that this mode of controlling the pilot valve of a hydraulic governor reduces overshooting to practically zero without the necessity for any ancillary compensating mechanism. I

One of the several objects of the present invention is to provide means whereby this self-compensating action may be produced in the first instance by the operation of the hydraulic governor shaft proper but wherein auxiliary valve means are provided to cooperate with the governor shaft and thus afford a wide range of choice in the pulsating frequency of pressure application to the power piston.

A further object of the invention is to provide readily adjustable selective means for varying the rapidity characteristic of the governor either by the manipulation of manually adjustable valve means or by varying the normal maximum governor pressure as determined by the adjusted setting of a pressure accumulator.

The present invention further contemplates a differenttially controlled speeder spring for opposing the centrifugal action of the governor fly-weights, whereby a common spring adjusting element may be controlled by a manual speed setting knob or by speed droop means operable from the power piston of the governor. The two adjustments of the speeder spring operate by means of differential gearing upon the common adjustable spring anchor of the speeder spring.

The present invention further provides centering spring means associated with the pilot valve and unstressed when the pilot valve is in a normal neutral position, the centering spring being stressed by movement of the pilot valve in either direction from neutral position so that the pilot valve is at all times spring-urged toward neutral position when it is displaced therefrom.

Means are further provided in the governor of the present invention for increasing the pulsating frequency of fluid pressure application ot the power piston when the displacement of the pilot valve by the centrifugal means exceeds a predetermined amount. In this way, a more frequent application of pulsating fluid pressure is provided when a sudden load change results in a major displacement of the pilot valve of the governor and much quicker governor response to sudden load changes is afforded.

It is to be understood that the broad principles outlined in the foregoing are not restricted in their application excepting as defined in the appended claims. However, by way of example, the present application sets forth preferred embodiments of the invention by way of example.

In the drawings:

Fig. l is a general schematic view of one form of the governor of the present invention;

Fig. 2 is a fragmentary cross-sectional view approximately on the line IIII of Fig. 1;

Fig. 3 is a vertical central cross-sectional view through a modified form of governor shaft and pilot valve;

Fig. 4 is a fragmentary vertical central cross-sectional view through a further modified governor shaft and bushing arrangement;

Fig. 5 is a cross-sectional view on the line V-V of Fig. 4; and

Fig. 6 is a further fragmentary vertical cross-sectional pump drive means.

view of the governor shaft and bushing arrangement of Fig. 4 but in a vertical plane at right angles thereto.

In the drawings the numeral designates a shaft which is connect-able with the engine or other device or system to be governed. The purpose and effect of the governor system is to maintain a constant velocity of shaft 10 despite changes in load, in the case'of an engine, or of other conditions tending to vary the velocity of the shaft 10. In the alternative, the governor serves to maintain a constant degree of speed droop; that is, a predetermined lessening of velocity with increases of load.

The system of the present invention provides novel means which are readily adjustable to vary the degree of speed droop, as occasion may require, including the ability to adjust the means to zero speed droop, in which case the velocity is maintained constant regardless of the load within predetermined maximum load limits. When the governor is set for zero speed droop, it is characterized as isochronous. Speed droop and the' ability to accurately regulate it are principally desirable when multiple prime movers are operating in parallel against a common load and it is desired that the load be uniformly distributed over the several prime movers.

Adjustment of the engine or other device or system being governed is accomplished by rotating a shaft designated 11 in the drawing and in the case of an engine the shaft 11 may be connected with the throttle valve or other fuel control means, as by means of an arm 12. In the case of engine governing operation the load on the engine is reflected in the angular setting of shaft 11.

The fly-weight head and the hydrodynamic fluid system which cooperates therewith operates in a housing 14 and comprises a shaft or sleeve 15 which rotates in a suitable bore -in the housing 14 and in the present instance is fixed to shaft 10 and may comprise a portion thereof,

theshaft 10 being driven by the engine being governed. It is usual to insert a resilient driving connection between the drive shaft and the governor mechanism proper in hydraulic governors, but in the present instance such a resilient driving connection is unnecessary because the governor arrangement of the present invention is found to eliminate hunting even under extreme conditions of operation.

Shaft 15 is'bored to receive a pilot valve 16 which has enlarged axially spaced valve heads 17. and 18 and is formed at its upper end with an enlargement 19 which cooperates to support a plurality of fly-weights 20. The fly-weights 20 are carried by arms 21 which have a common pivot 22 at the outside of shaft 15. The arms 21 are pivotally engaged by links 23 which are also pivotally connected to the enlargement 19 of pilot valve 16 as at 24.

From the foregoing it will be clear that any tendency of centrifugal force to move the fly-weights outwardly, upon increase in speed of the shafts 10 and 15, tends to straighten the toggles which the arms 21 and the links 23 form, and this results in lowering movement of the valve 16 in the bore of the shaft 15. A decrease in speed, evidenced by a tendency of the fly-weights to move inwardly toward the shaft 15, tends to collapse the toggles, and the links 23 accordingly raise the pilot valve 16 in the shaft 15. The pilot valve 16 rotates with shaft 15 but is free to move axially therein.

The necessary hydraulic pressure required for operation of the governor is provided by a pump indicated at 25, which may be arranged to be drivenfrom shaft 10 by a pair of gears 27 and 28. The pump is preferably of the reversible type wherein the output is unidirectional regardless of the direction of rotation of the accumulator 29, which will be described in greater detail later herein, by means of a conduit 30, and a conduit 31 extends from the accumulator 29 to the housing element 14, where it communicates with a peripheral passage or opening 32 in shaft 15, whereby conduits 30 and 31 The pump communicates with an 4 have continuous and uninterrupted communication with the space between valve heads 17 and 18.

The housing 14 has a pair of passages 37 and 38 and shaft 15 is provided with a pair of peripheral passages or openings 39 and 40 which are normally axially in registry with the valve heads 17 and 18 and also in axial registry with the passages 37 and 38 of housing14, as illustrated in Fig. 1. Passages 37 and 38 communicate, respectively, with the upper and lower side of a cylindrical chamber 40 formed in housing 14. A power or actuating piston 42 is disposed in chamber 40 and has a piston rod 43 which connects with an arm 44 secured to shaft 11. In this way axial movement of piston 42 in chamber 41) produces rotative movement of shaft 11 and thus the movements of piston 42 directly determine and reflect the load setting of shaft 11, or any other variable condition which shaft 11 may serve to adjust.

Shaft 15 is formed with a peripheral outlet passage above upper valve head 17 and a second peripheral outlet passage 51 below lower valve head 18. The outlet passages 50 and 51 of shaft 15 are in axial registry with a pair of outlet passages 52 and 53, respectively, formed in housing 14.

In a general way, it will be seen from the foregoing .1 that acceleration of shaft 10 will, by increased centrifugal force on fly-weights 20, lower pilot valve 16 and, by lowering of valve head 18, connect conduit 31 with conduit 38. This directs fluid pressure against the lower side of piston 42 and accordingly rotates shaft 11 in a counterclockwise direction to decrease the fuel setting, in instances where an engine is being governed, to accomplish the necessary slowing of shaft 10 to the predetermined speed level. At the same time that conduit 38 is connected with fluid pressure supply conduit 31, conduit 37 is connected with outlet passage 52 by reason of the lowering of valve head 17.

It will be understood by those skilled in the art that the entire mechanism of the drawing may be housed'in a suitable casing of any form whose bottom may be used as a sump for pump 25, whereby all discharge outlets of the system discharge openly into the casing, where they gravitate to the sump for re-use by the pump. The sump is indicated schematically at 54 in the drawing.

In Fig. l the numeral 55 designates a coil spring whose upper end is fixed to the under side of valve head 18 of pilot valve 16 and whose lower end is fixed to a block 56, the latter being fixed relative to shaft 15 by means of a set screw 57. Spring 55 is an extension-compression spring and in the position illustrated in Fig. l is unstressed. It serves to continuously urge pilot valve 16 to its neutral position where passages 39 and 40 are blocked by valve heads 17 and 18. Spring 55 damps out oscillations of the pilot valve due to any irregularity in the governor drive and also insures the return of the pilot valve to its normal neutral position as the engine returns to proper speed after a governing correction.

When proper speed obtains, according to the speed setting of the governor, a state of equilibrium exists between the centrifugal force of the fly-weights, urging pilot valve 16 downwardly, and an extension spring 60, known in the art as a speeder spring. The lower end of spring is anchored to the top of enlargement 19 of the pilot valve and the upper end of the spring in anchored .to a part 61 which is journaled for free rotation in a block 62, the latter being fixed to the lower end of a vertically adjustable bar 63.

Bar 63 has fixed thereto a pin 68. upon which a gear 69 is journaled for free rotative movement, and gear 69 is in meshing engagement with a pair of rack bars 70 and 71, which are likewise slidably supported by the Wall portion 64 of the governor casing. Racks 70. and 71 hold gear 69 against movement, excepting by and upon vertical adjustment of one or the other of racks 70 and 71. Rack 71 has a further toothed rack portion 72 in meshing engagement with a pinion 73. Pinion 73 is fixed to a speed setting shaft 74 journaled in a wall portion of the governor casing and externally thereof shaft 74 is provided with a manual speed setting knob (not shown).

Assuming rack 70 to be stationary, clockwise adjustment of speed setting shaft 74, as viewed in Fig. 1, counterclockwise as viewed by one manipulating the speed setting knob, causes rack bar 71 to move upwardly, and pinion 69 likewise moves upwardly by planetary or differential action along rack bar 70, and in this manner speed setting of the governor is increased by an increase in the tension of speeder spring 60.

Speed droop is controlled by vertical movements of rack bar 70. A lever 80 is pivoted at one end to piston rod 43 asat 81 and has a slot 82 at its opposite end. In Fig. 1, the numeral 83 designates schematically a sliding fulcrum which is adjustable in any desired manner from right to left as viewed in Fig. 1, and carries a fulcrum pin 84 which engages in slot 82 of lever 80. The lower end of rack bar 70 likewise carries a pin 86 which engages in slot 82.

Pins 84 and 86 engage slot 82 from opposite sides of lever 80 and each extends only part Way into the slot so that fulcrum 83 may be adjusted to the left, as viewed in Fig. 1, until pin 84 is coaxial with pin 86. In the position just described, that is with pins 84 and 86 coaxial, vertical movements of power piston 42 will oscillate lever 80 about the common axis of pins 84 and 86 but will impart no movement to rack bar 70 and accordingly no speed droop will be introduced with changes in the load of the engine being governed and the governor will be isochronous.

When sliding fulcrum 83 is adjusted so that pin 84 engages slot 82 to the right of pin 86 at any desired position up to the maximum illustrated in Fig. 1, upward movement of the power piston 42 to decrease fuel to correct for an increase in speed will move rack bar 70 upwardly and thus move gear 69 and bar 63 upwardly to increase the speed setting in a predetermined proportion -with respect to the decreased load as evidenced by the tendency of shaft to increase speed.

A reduction in the speed setting of speeder spring 60 due to an increase in load as evidenced by downward movement of piston 42 is effected in a reverse manner to that just described.

The novel mode of compensation set forth herein by way of example will now be described, that is, the means employed to eliminate objectionable hunting" during the course of a governor adjusting operation. In the governor shown in Fig. l shaft has a single peripheral opening 39 and a single peripheral opening 40. Therefore, these openings will pass their respective passages 37 and 38 just once during each rotation of shaft 15. The result of the operation of this much of the apparatus, when pilot valve 16 is displaced, would be to transmit to either of passages 37 or 38 one shot or jet of hydraulic pressure during each rotation of shaft 15, and these intermittent bursts of pressure are found to provide an ideal mode of compensation without resort to the usual complicated compensating systems.

With the foregoing construction of shaft 15, as has been said, one intermittent application of pressure will result from each rotation of shaft 15. In the form of our invention illustrated in Fig. 1, means are provided for further reducing the frequency of pressure application which effects more desirable compensating action in many applications and ranges and capacities of governor design and operation.

Referring to Fig. 1, the numeral 90 designates a rotary valve journaled in housing 14 and extending across the passages 37 and 38. Valve 90 has a pair of transverse passages 91 and 92 in registry with passages 37 and 38 and, as is clearly shown in Fig. 2, the passages 37 and 38 extend angularly and the passages 91 and 92 likewise extend angularly.

As a result of this arrangement the passages 91 and 92 permit fluid flow through their respective passages 37 and 38 only once during each full rotation of valve 90, rather than twice as would be the case if the passages 37, 33, 91 and 92 were all straight and diametral of valve 90. Continuous rotation of valve 9t) in timed relation with shaft 15 is obtained by gears 94 and 95 which mesh with each other and are fixed to shaft 10 and rotary valve 90, respectively.

It is apparent from the foregoing that hydraulic fluid pressure from passage 32 will be communicated to the power piston chamber 40 only when passages 39 and 40 and passages 91 and 92 are in connecting relation with passages 37 and 38 simultaneously.

If we assume that gears 94 and 95 are so proportioned that pilot valve 90 is rotated one and three-fourths rotations for each rotation of shafts 1t and 15, and if we begin with passages 39 and 4t and passages 91 and 92 in communicating registry, then the communicating registry will re-occur only after shafts 1d and 15 have made four full rotations, during which period valve 99 will make seven rotations. This will give a strong compensating action.

Obviously, the foregoing principles may be varied widely to give a wide range of frequencies in the pulsating governing action and may thus vary the degree of compensation to satisfy a wide variety of practical applications of the hydraulic governor of the present invention.

With further reference to Fig. 1, a further rotatably adjustable valve 98 is journaled in housing 14 and extends across the passages 37 and 38 and has transverse passages 99 and 130 connecting at opposite sides with the passages 37 and 38, respectively. Valve 98 has a manipulating knob 101 at its upper end for rotary adjustment thereof and a lock nut 162 retains valve 98 in properly adjusted position.

The position of adjustment of valve 98, which is shown fully open in Figs. 1 and 2, determines the efiective crosssectional areas of passages 37 and 33 and this controls the rapidity with which actuating or power piston 42 responds to changes in velocity of the input shaft 14) and thus permits selective adjustment of the governor characteristic which is termed rapidity by those skilled in the art. Rapidity is a term denoting the speed with which the actuating piston moves from one fuel setting to another. Instances where best regulation is attained by free and accurate adjustment of rapidity are found in the control of prime movers, notably two-cycle gas engines.

As mentioned previously, pressure accumulator cham ber 29 is interposed between pressure supply conduits 3t and 31 and contains a pressure piston 105 backed by a compression coil spring 106. Spring 136 seats at its other end against a block 107, the position of which in the accumulator is normally determined by a pair of set screws 108. In Fig. 1 the numeral designates an outlet passage from accumulator 29 which is exposed when piston 105 moves upwardly under the force of excess pressure in accumulator 29 to permit liquid flow therefrom and consequent pressure regulation.

The setting of set screws 1'88 determines the pressure limit at which piston 105 will move to vent or discharge excess pressure through passage 110 and thus determine the minimum upper limit of pressure. Means are provided for increasing this upper limit to speed up the action of the governor by increasing the pressure limit of the governor over the normal rated working capacity pressure established by set screws 198. Such means may comprise a stem 112 which is threaded into wall portion of the governor casing and has a manual adjusting knob 113 at the exterior of the casing.

By screwing stem 112 downwardly as viewed in Fig. 1 its lower end engages block 107 and rnoves it downwardly away from set screws 108 and thus requires a greater hydraulic pressure force against piston and spring 106 before me outlet passage 11) is exposed, thus increasing the maximum pressure setting. The higher pressure thus available in conduit 31 thus increases the amount of liquid transferred to the power piston chamber 40 during each of the intermittent shots or jets and thus regulates the step the power piston 42 takes for each shot, in the manner similar to that of the rapidity regulating valve 93.

Reference will now be had to the modified form of the present invention illustrated in Fig. 3 wherein provision is made, among other things, to balance side thrust on the pilot valve. This is accomplished by providing opposed openings at opposite sides of the shaft which eliminates the side thrust but this requires that other provision be made to maintain the proper periodic pulsating hydraulic pressure action heretofore described.

Referring to Fig. 3, the numeral 114 designates a housing element similar to the one designated 14 in Fig. 1; the numeral 116 designates a pilot valve, similar to pilot valve 16 of Fig. 1, having valve heads 117 and 118; and the numeral designates a governor shaft similar to shaft 15 of Fig. l;

A stationary bushing 121) is interposed between shaft 115 and the bore in housing 114. Inlet pressure passage 131 corresponds to pressure passage 31 and passages 137 and 138 to the power piston chamber (not shown) correspond to passages 37 and 38, respectively, of Fig. 1. Pressure passage 131 extends through bushing and is in constant communication with the space between valve heads 117 and 118 by virtue of an external annular groove 140 and a radial passage 141 leading therefrom, both formed in shaft 115.

.Shaft 115 is also formed with radial outlet passages 143 and 144 above valve head 117 and below valve head 118, respectively, and these passages communicate with external annular grooves 145 and 146, respectively, which in turn communicate with outlet passages 147 and 148 which extend through bushing 120 and housing 114.

Instead of the single lateral radial openings 39 and 40 of shaft 15 of Fig. 1, the shaft 115 of the present embodiment is provided with opposed pairs of radial openings. 150 and 151 normally in registry with valve heads 117 and 118. These radial openings periodically come into registry with pairs of lateral openings 153 and 154 formed in bushing 120 and bushing 120 is further provided with annular grooves 155 and 156 which place openings 153 and 154 in constant communication with passages 137 and 138 of housing element114.

It will be seen from the foregoing that, when pilot valve 116 displaced, as illustrated in Fig. 3, pressure will be applied to the pair of passages 151 and that pressure will be communicated to the pair of passages 154 of bushing 120 once during each half rotation of shaft 115. Because of the non-linear extent of passage 91 in rotary valve 90, this will notdisturb the previously described operation wherein pulsating pressure is communicated to the power piston chamber only once for each four rotations of shaft 115.

The effect of the embodiment of Fig. 3 is to eliminate objectionable side thrust, the pulsating frequency being the same as in the case of Fig. 1. Obviously, if pilot valve 116 be displaced upwardly, instead of downwardly as illustrated in Fig. 3, a reverse application of pulsating hydraulic pressure to the power piston will result.

Figs. 4, 5 and 6 illustrate a further innovation which provides a more rapid governing action when the pilot valve is subject to a major displacement due to a sudden load change. -In the illustration of this embodithe spaced valve heads of the pilot valve.

ment of the invention, the pilot valve is omitted to give greater clarity of illustration to the several passages. However, it is to beunderstood that the pilot valve is identical with those illustrated and described in the preceding embodiments.

Referring :to Figs. 4 through 6, the numeral 214 designates a housing analogous to housings 14 and 114, 215 designates a fixed bushing, and 216 designates a governor shaft which rotates in bushing 215 and in which the pilot valve operates. A pressure supply conduit is indicated at 217 and a radial passage 218 leads therefrom through bushing 215 to an external annular groove 220in shaft 216 and one or more radial passages 221 lead inwardly from groove 220 to the space between the pilot valve heads.

Passage 237 and 238 correspond to the lower piston chamber pressure supply passages previously described and rotary valve 240, extending across passages 237 and 238 and having openings 241 and 242 in registry therewith, respectively, correspond withrotary valve 90 of Fig. 1, being similarly connected for rotative movement with shaft 216.

Shaft 216, bushing 215 and housing 214 are formed with outlet passages (notshown) above and below the pilot valve heads, the outlet passages being identical in location, arrangement and operation as the outlet passages designated 143 through 148 in Fig. 3.

Shaft 216 isalso provided with opposed pairs of radial openings 245 and 246 normally in registry with As in the case of Fig. 3, these openings periodically come into registy with pairs of lateral openings 247 and 248 formed in bushing 215 and bushing 215 is further provided with external annular grooves 250 and 251 which place openings 247 and 248 in constant communication with passages 237 and 238, respectively, of housing element 214.

The operation and resultof so much of the construction as has thus far been described is identical with the structure and operation of the embodiment of Fig. 3. In the embodiment of Figs. 4 through 6, in addition to the power piston supply passages 237 and 238, there is a second pair of power piston supply passages 255 and 256 which bypass the rotary valve 240, leading directly to. opposite ends of the power piston chamber.

Staggered between the openings 245 and 246 of shaft 216 are pairs of smaller openings 258 and 259 in axial alignment with the openings 245 and 246, respectively. Openings 258 and 259 communicate with axially extending passages 260 and 261, respectively, which register in passing with pairs of openings 262 and 263 in bushing 214, the latter being in constant communication with the alternative power piston chamber passages 255 and 256 by reason of external annular grooves 264 and 265 formed in bushing 215.

The operation of the embodiment of Figs. 4, 5 and 6 will now be described. Upon a minor displacement of the pilot valve, openings 245 and 246 will be exposed, one for pressure connection and the other for outlet connection, but the smaller openings 258 and 259 will not be exposed. Thus the operation of the governor, including the cooperation of rotary valve 240, will be identical with that described in conjunction with the embodiment of Fig. 3.

However, on a large load change openings 258 and 259 will also be exposed by the pilot valve heads, and

covering of openings 258 and 259 by the pilot valve heads, whereupon the governing operation will proceed to its conclusion exactly as in the case of the embodiment of Fig. 3.

What is claimed is:

l. A governor mechanism comprising a pressure chamber and a regulator movable therein in response to differential pressure, a fluid passage communicating with the pressure chamber, a rotary member and a bearing support therefor, a pilot valve movable axially in said support in response to changes in speed in the rotary member, an opening in said rotary member and means on said pilot valve normally blocking said opening, speed responsive means actuable by said rotary member for controlling axial movements of said pilot valve, said fluid passage leading to said rotary member in axial registry with said opening whereby upon displacement of the pilot valve said opening is exposed to said passage intermittently as said opening passes the fluid passage during rotation of the rotary member, a rotary valve across said passage to close and open said passage intermittently, and means connecting the rotary member and the rotary valve for timed rotation at unequal speeds, whereby the frequency of simultaneous open condition of the passage at the rotary member and at the rotary valve is a submultiple of the rotative speeds of the rotary member and the rotary valve.

2. A governor mechanism comprising a pressure chamber and a regulator movable therein in response to differential pressure, a source of fluid pressure and a fluid passage connecting the pressure chamber and the source of fluid pressure, a rotary member and a bearing support therefor, a pilot valve movable axially in said support in response to changes in speed in the rotary member, an opening in said rotary member in axial registry in said fluid passage and means on said pilot valve normally blocking said opening, speed responsive means actuable by said rotary member for controlling axial movements of said pilot valve, whereby upon displacement of the pilot valve said opening opens said passage at the rotary member intermittently as said opening passes the fluid passage during rotation of the rotary member, a rotary valve across said passage to close and open said passage intermittently, and means connecting the rotary member and the rotary valve for timed rotation at unequal speeds, whereby the frequency of simultaneous open condition of the passage at the rotary member and at the rotary valve is a submultiple of the rotative speeds of the rotary member and the rotary valve.

3. A governor mechanism comprising a pressure chamher and a regulator movable therein in response to differential pressure, a fluid passage communicating with the pressure chamber, a rotary member and a bearing support therefor, a pilot valve movable axially in said support in response to changes in speed in the rotary member, an opening in said rotary member and means on said pilot valve normally blocking said opening, speed responsive means actuable by said rotary member for controlling axial movements of said pilot valve, said fluid passage leading to said rotary member in axial registry with said opening whereby upon displacement of the pilot valve said opening is exposed to said passage intermittently as said opening passes the fluid passage during rotation of the rotary member, other means for closing and opening said passage intermittently, and means connecting the rotary member and said other means for timed movement, the frequency of opening and closing of said other means being unequal to the rotative speed of the rotary member, whereby the frequency of open condition of the passage is a submultiple of the rotative speed of the rotary member.

4. A governor mechanism comprising a pressure chamber and a regulator movable therein in response to differential pressure, a source of fluid pressure and a fluid passage connecting the pressure chamber and the source of fluid pressure, a rotary member and a bearing support therefor, a pilot valve movable axially in said support in response to changes in speed in the rotary member, an opening in said rotary member in axial registry in said fluid passage and means on said pilot valve normally blocking said opening, speed responsive means actuable by said rotary member for controlling axial movements of said pilot valve, whereby upon displacement of the pilot valve said opening opens said passage at the rotary member intermittently as said opening passes the fluid passage during rotation of the rotary member, other means for closing and opening said passage intermittently, and means connecting the rotary member and said other means for timed movement, the frequency of said other means being unequal to the rotative speed of the rotary member, whereby the frequency of open condition of the passage is a submultiple of the rotative speed of the rotary member.

5. A governor mechanism comprising a pressure chamber and a regulator movable therein in response to differential pressure, a fluid passage communicating with the pressure chamber, a rotary member and a bearing support therefor, a pilot valve movable axially in said support in response to changes in speed in the rotary member, opposed radial openings in said rotary member and means on said pilot valve normally blocking said openings, speed responsive means actuable by said rotary member for controlling axial movements of said pilot valve, said fluid passage leading to said rotary member in axial registry with said openings whereby upon displacement of the pilot valve said openings are exposed to said passage intermittently as said openings pass the fluid passage during rotation of the rotary member, a rotary valve across said passage to close and open said passage intermittently, and means connecting the rotary member and the rotary valve for timed rotation at unequal speeds, whereby the frequency of simultaneous open condition of the passage at the rotary member and at the rotary valve is a submultiple of the rotative speeds of the rotary member and the rotary valve.

6. A governor mechanism comprising a pressure chamber and a regulator movable therein in response to differential pressure, fluid passage means communicating with the pressure chamber, a rotary member and a bearing support therefor, a pilot valve movable axially in said support in response to changes in speed in the rotary member, an opening in said rotary member and means on said pilot valve normally blocking said opening, a source of fluid pressure and passage means connecting the same with said opening when the pilot valve is axially displaced, speed responsive means actuable by said rotary member for controlling axial movements of said pilot valve, said first fluid passage means leading to said rotary member in axial registry with said opening whereby upon displacement of the pilot valve to expose said opening fluid pressure is transmitted to the pressure chamber in intermittent jets as said opening passes said fluid passage means during rotation of the rotary member, another opening in said rotary member of lesser axial extent than the first-mentioned opening, the centers of said two openings being on the same transverse plane through the rotary member whereby said other opening is exposed only upon a major displacement of the pilot valve to increase the frequency of the intermittent pressure jets during such major displacement.

7. A governor mechanism comprising a pressure chamber and a regulator movable therein in response to differential pressure, a fluid passage communicating with the pressure chamber, a rotary member and a bearing support therefor, a pilot valve movable axially in said support in response to changes in speed in the rotary member, an opening in said rotary member and means on said pilot valve normally blocking said opening, a source of fluid pressure and passage means connecting the same with said opening when the pilot valve is axially displaced, speed responsive means actuable by said rotary member for controlling axial movements of said pilot valve, said first fluid passage means leading to said rotary member in axial registry with said opening whereby upon displacement of the pilot valve to expose said opening fluid pressure is transmitted to the pressure chamber in intermittent jets as said opening passes the fluidpassage during rotation of the rotary member, a

a rotary valve across said first fluid passage to close and open the same intermittently at an unequal frequency relative to velocity of the rotary member whereby the frequency of simultaneous open condition of said passage at the rotary member and at the rotary valve is a submultiple of the velocity of the rotary member, another opening in said rotary member of lesser axial extent than the first-mentioned opening, the centers of said two openings being on the same transverse plane through the rotary member whereby said other opening is exposed only upon amajor displacement of the pilot valve, said other opening having connection with the a pressure chamber independently of the rotary valve to increase the frequency of the intermittent pressure jets during such major displacement.

References Cited in the file of this patent UNITED STATES PATENTS

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