US2467445A

US2467445A - Governor apparatus

Info

Publication number: US2467445A
Application number: US568436A
Authority: US
Inventors: Anthony F Schwendner
Original assignee: Westinghouse Electric Corp
Current assignee: CBS Corp
Priority date: 1944-12-16
Filing date: 1944-12-16
Publication date: 1949-04-19
Anticipated expiration: 1966-04-19

Description

April 195 1949 A. F. scHwENDNl-:R 2,467,445

GOVERNOR APPARATUS OIL PRESSURE I ATTORNEY April 19, 1949.. A. E. s-cHwENDNl-:R 2,467,445

'GOVERNOR APPARATUS 4 sheets-sheet 2 Filed D90. 16, 1944 D lll u lL ln en PRESSURE F' 1G. 9.

. INVENTOR ANTHQNY F. SCHWENDNER BY l w. Ucw.,

ATTORNEY lApril 19, 1949. v A. F. SCHWENQNER 2,467,445

GOVERNOR APPARATUS Filed Dec. 16, 1944 4 Sheets-Sheet 3 32. 5o an 68 s\ ,s )o sa as FlCzO.

75 il. un sa s@ z 'IPO 'l e* lq. v19a l Q; l se 3l 5' as I8 l ,9 6i e? 69 s @l lOl Fredi.

DVI @1M ATTORNEY April 19, 1949. A. scHwENDNER 2,467,445

GOVERNOR APPARATUS A Filed Dec. 16,A 1944 4 Sheets-Sheet 4 INVENTOR ANTHONY' F. SCHWENDNER.

BY I. ITI-GAE. www

ATTORNEY Patented Apr. 19, 1949 UNITED STATES l PATENT lQFFICE y y 2,467,445 l y GovRNon APPARATUS Anthony F. Schwendner, RidleyA Park,`1?a assignr to Westinghouse Electric `Corporaton,'East Pittsburgh, Pa., a corporation of Pennsylvania Application December 16, 1,9144, Serial No. 568,436

'z claims. zegel-:14)

1 The invention relates to a governor of the pressure transformer type, and it has for an object to provide apparatus of this character including y a flyweight aggregate comprising flyweights and a leaf spring With the centrifugal force of the flyweights opposing force of the spring to develop a couple for applying force to the valve member of the transformer and which force cooperates with force applied to the latter due to transformed or liquid pressure in order to Vary the transformed or governing liquid pressure dependent upon speed.

A further object of the invention is to provide apparatus of the above character which is adjustable to provide a desired range of governing speeds.

Another object of the invention is to provide a centrifugal governor including flyweights connected to a rotary driving member by a leaf spring, with the spring extending transversely of the axis of the driving member and the weights arranged to deflect the spring laterally under the influence of centrifugal force.

These and other objects are effected by the invention as will be apparent from the following description and claims taken in connection with the accompanying drawings, forming a part of this application, in which:

Fig. 1 is a view showing a turbine partly in section with the improved governor applied thereto and arranged to provide transformed or governing pressures which increase as the turbine speed increases;

Fig. 2 is an enlarged sectional view of the governor of Fig. 1;

Fig. 3 is a diagram pertaining to Fig. 1;

Fig. 4 is a sectional view taken along the line IV-IV of Fig. 2;

Fig. 5 is a detail view of the flyweight leaf spring;

Fig. 6 is a sectional view taken on the line VI-VI of Fig. 5;

Fig. 7 shows a modified form of the apparatus shown in Fig. 1;

Figs. 8 and 9 are views similar to Figs. 2 and 3, but showing an arrangement wherein the governing or transformed pressure decreases as the speed decreases;

Fig. 10 is a sectional view showing a modified form of the transformer;

Fig. 1l is a view generally similar to Fig. '7, but showing the addition of means for adjusting the speed range;

Fig. 12 is a diagrammatic view illustrative of anoperation involved; ig. 1

Fig. 13is a sectional view similar to Fig. 11, but

s." showing 'meded features; and

Figs. 14 and 15 are diagrammatic views illustrative of 4principles involved with the jdirect (Figs. 1, 2 and 3) and inverse (Figs. 8 and 9) ...forms ofthe governor.

In Figgl of the'drawings, there is shown en v-relastic fluid turbine Shaving a motive fluid ad- .mission valve 6 forming a part of a movable' com- .'ponent having a piston or pressure area 1 to which liquid under governing pressure is applied against the force of the spring 8.

, The turbine includes a rotary member or shaft lll extending into'a casing structure Il providing a' chamber l2. Within the chamber, the

Y f drive shaft isfprovided Ywith a composite body or head structure, at I3, carrying the leaf spring I4, theflywei'ghts l5 attached to opposite sides of the leaf spring, and the transformer valve or relay member I6 (Figs, l, 2, 8, 11 and 12),!I6a jiFig. '7), 0r Iii?)` andV |60l (Figs. 10 and 13) by means ofwhich the transformed or governing liquid pressure is changed.

shown, the casing structure is formed to accommodate the gear pump, including the gear AIlcOnnected-to the drive'shaft IU andtheidler gear i8 meshingtherewith. The outlet passage I9` of the pumpois arranged Sto discharge oil i through the orice 20to the governing or. transformed pressure space, at 2li, the latter preferably including, as shown in Figs. y1, 2,8 and 11, .f the axial bore 22 formed in the drive shaft, the

passage of the servo-motor supply conduit 23.,.and

l the pressure spacey 24 of the pressure-responsive seat2'l encompassing thel discharge end or port portion 28 of the bore 22, and with which theurim 2!!` of thejcup valve I6 cooperates to provide an f annular orice controlling the pressure of oil in the transformed or governing pressure space. A

rvery small movement of the transformer or cup valve toward and away `from the seat. suffices to g provide an annular orifice now areaA range for governing pressure` variation over a suitable range.

The body or head structure, at I3, includes the Yfange 3l connected to the drive shaft, a spacing 5. member 32-providingmclearance space 3 3 for one ofthe rotating flyweights i5, thelspacing 'memi -qberhaving en d ring portions and vvv35, and a 'ring-ft {incensiringtonen 3,4 gesaneerd by therebetween.

screws 31 to the flange 3| and the ring 36 is attached to the end ring portion 35 to clamp the leaf spring I4 to hold the latter in position relative to the head structure.

The transformer cup valve I6 is preferably carried by a plunger 39 arranged coaxially with the drive shaft l and guided by the bore 40 formed in the part 4| positioned by the counterbore 42 formed in the flange 3|, so that the bore 4U is in axial alignment with the drive shaft, A screw 43 detachably connects the part 4| to the flange. With the guide part 4| and the plunger carried by the flange 3|, it will be apparent that these elements rotate with the drive shaft which is the preferred construction, as shown in Figs. 1, 2, 8 and 11.

Oil escaping through the annular orifice provided by the cup valve rim 29 and the seat 28 enters the annular space 44 and flows from the latter through the ports 4-5 formed in the flange 3| to the annular chamber 46 which discharges through the passage 4l to the interior of the chamber l2 whose bottom is connected by a drain opening passage 48 to the sump 49 supplying the pump suction pipe |9a.

The leaf spring |4 includes outer and inner attachment portions 50 and 5| joined by a flexible portion 54. The outer attachment portion is 'connected to the drive shaft so that the leaf spring extends substantially in a rotational plane of the latter and intersects the axis of rotation thereof. The outer attachment portion 50 is preferably secured to the drive shaft by being clamped between the ring portion 35 and the ring 36.

The flyweights I are disposed at opposite sides of the inner attachment portion 5| of the leaf spring and they are preferably provided with feet 52 connected by screws 53 to clamp the leaf spring The intermediate portion 54 of the leaf spring is free to flex to provide for movement of the spring and weight aggregate toward or away from the transformer valve I6, |5a, or |517. A maximum length of intermediate spring portion 54 for bending is provided by the clear,-

ance spaces 52a of the feet and the rounded portions 35a and 36a of the ring portion andring for anchoring the outer end of the spring, whereby the small amount of total bending is distributed over a substantial length and excessive bending -or stresses .at any point are avoided.

The flyweights |5 are not only located at opposite sides of the leaf spring but they are arranged to have their centers of gravity spaced `acting on the leaf spring to apply force to the valve member. More particularly, the centers of gravity of the Weights are in an axial plane of the drive shaft which bisects the flexible portion "x 54 in the direction of its length, that is, in a'plane which is the plane of symmetry of the leaf spring.

As the weights are connected together as a unitary Lstructure by the means connecting them to the leaf spring, the centrifugal force of one weight f lbalances that of the other except for the centrif- 'i ugal couple effective to apply force to the relay.

By way of example, the leaf spring is shown as formed from a disc element which is cut out arcuately, at v55, as shown in Fig. 5, to provide an outer ring portion 56 joined by the flexible portion 54' to the inner portion 5|, and the annular portion is clamped in place between the ring portion and the ring, as aforesaid.

Increase in force applied to the plunger and the cup valve, due to the couple Aapplied to the spring on account of centrifugal force of the weights overcoming the force of the spring, is opposed by increasing liquid pressure force acting on the valve member IG, or increase in the couple due to centrifugal force may be accompanied by decrease in governing or transformed liquid pressure. In Figs. l, 2, 7, 10 and 13, the couple, due to centrifugal force of the yweights, tends to deflect the leaf spring toward the transformer to increase the transformed or governing liquid pressure. On the other hand, with the .arrangement shown in Figs. 8 and 11, where an increase in speed is accompanied by a decrease in transformed or governing pressure, the effect of an increase in the couple due to centrifugal force of the flyweights -acts in a direction to permit the valve member to move outwardly under the influence of force of liquid pressure applied thereto to lower the transformed or governing pressure.

While the cup valve relay plunger 39 is preferably carried by and is rotatable with the drive shaft, as shown in Figs. 1, 2, 8 and 11, it may be carried by the stationary structure so that the drive shaft is rotatable relative thereto, as shown in Fig. '7. In the latter view, the casing has a stationary head 4|a providing a cylindrical guide 40a for the plunger 39a provided with the cup valve |60. cooperating with the escape port 28a of the governingv liquid pressure space, at `2|a, such space being supplied with liquid through an orifice 20a from a gear pump, as heretofore described. A thrust-transmitting ball 62 is preferably arranged between the spring and weight aggregate and the end of the plunger remote from the cup valve.

While the governing arrangements hereinbefore described are of the constant speed type, the speed may be adjusted over a suitable percentage by adjustment of the load spring 8 for the movable component 25 of the pressure-responsive means of Fig. 1, manually-operable mechanism 54 being shown for making this adjustment.

In Figs. 10 and 13, there are shown piston relay type transformer valves |6b and |6c which operate to achieve the purposes of the -cup valve already described. The relay valve |612 of Fig. 10 has a piston or land portion 61 which justlaps the transformed or governing pressure port 68. The slightest movement of the valve member from the lapped position in one direction places the highpressure port 59 in communication with the transformed pressure port` 68 to increase rthe transformed pressure, and, in the other direction, to place the transformed pressure port in communication with the exhaust port 10 to reduce the transformed or governing pressure. While the loperating'principle of Fig; 14 is the same, it

differs in structural detail, the relay piston valve IEC having spaced 'lands 1| and '|2whose inner edges just lap the pressure and exhaust ports 59a and 10a.

The relay valve I 6b or |6c has a piston face 13 or 13a at one end, presenting an area to the transformed or governing liquid pressure in the space, at 2lb or at2|c, so that the force due to such pressure is applied to the relay and tending to move the latter to place the transformed pressure space in communication with the exhaust port 10 or 10a to lower the transformed or governing pressure. Thus, it will be seen that change in force applied to the relay and due to the couple of the flyweights is accompanied by change in transformed or liquid pressure force applied to the relay in opposed relation, an increase in the couple of the flyweights due to centrifugal force and in consequence of an increase in speed and tending to move the relay in a direction to increase the transformed pressure is met by an opposing force tending to move the relay in the opposite direction. On the other hand, a decrease in the couple of the flyweights, due to a decrease in speed and consequent decrease in the force applied to the relay, results in the transformed liquid pressure force acting on the latter moving the relay in a direction to reduce the transformed or governing pressure.

Fig. 13 also differs over Fig, l0 in the way in which liquid from the transformed pressure space is applied to the relay piston valve to exert force thereon in opposition to centrifugal force. The transformed pressure space, at 2Ic, between the lands 'II and 'i2 is connected by a passage 'I5 eX- tending through the land 'I2 to the equalizing space 'I6 to which the piston valve pressure area 13a is exposed. The passage I5 preferably has a suiiiciently small flow area to function as an orice to introduce a time element to provide for stability.

In Fig. 11 the leaf spring aggregate has a load spring 18 associated therewith and providing for speed range adjustment of the governor, the spring 'I8 having a follower 'I9 which is adjustable in opposite directions by means of the hand-controlled screw 89 carried by the casing structure I Ia. The transformed governing pressure is supplied to a pressure-responsive device, at 8|, including an operating cylinder S2 with an operating piston 83 therein, the transformed pressure acting on the piston 83 so as to move the admission valve 8l! connected thereto in an opening direction, such movement being opposed by the spring 85 acting on the piston 83 in the opposite direction. The spring 85 is adjustable by means of the hand-controlled screw 86 to provide for a suitable percentage of speed range adjustment, for example, for a twenty per cent adjustment of speed range. The considerable amount of centrifugal force change acting on the yweights I5 in case of wide speed range requires, for governing over a wide speed range, that change in centrifugal force shall be balanced by spring compression afforded by the spring 'I8 adjusted by the screw 89. As a change in spring force is represented by a change in transformed pressure applied to the pressure area I of the piston 83 and to the area presented by the relay cup valve, such change in force is accompanied by change in force acting on the piston area 'I in the ratio of the cup valve and piston areas.

To facilitate accurate relative positioning of the relay and the spring and weight assembly, the latter is preferably provided with a threaded abutment 88 carried by the assembly and which is adjustable to secure the desired relative positioning.

The improved governor is susceptible of being dealth with as a unit apart from the apparatus in connection with which it is used, thereby facilitating manufacture, servicing, and replacement. To this end, as shown in Fig. 11, the casing IIa has a depending portion 93 providing the sump 49a; and, at its inboard end, the casing is joined to a body 94 having a flange 95 connected by screws 96 to the machine casing 9'I so as to cover the opening 98 formed in the latter, The body is formed with a cylindrical bearing opening 99 for the stub shaft Ilia connected by the spline coupling |99 to the turbine 0r machine shaft lil. A housing member lill is attached to the inner end of the body 94 to provide a chamber for the gear pump including the gears |I and I8. The stub shaft ina is formed with the axial bore 22, as heretofore described, the bore forming a part of the transformed pressure space, at 2|, and being provided, at its outer end, with an escape port with which the cup valve I6 cooperates. The body and the housing are formed with all necessary passages, including the suction and discharge passages lsb and I9 for the pump, the passage I9 being provided with the orifice 2U for supplying liquid to the transformed pressure space as well as to the load relief valve 26 and with the passage 23a connected by the pipe 23 to the displacement chamber 24a of the servomotor apparatus, at 8 I.

From the structure just described, it will be apparent that the casing IIa, the governing mechanism therein, the body 9A, the gear punip, and the operating stub shaft I (la constitute a unit assembly, at |04, which may be handled as a unit, it being merely necessary to connect and disconnect the piping and attach and detach the body 9d to the casing 9'I incident to assembly and removal thereof with respect to the latter, the spline coupling Ill permitting of connection and disconnection of the sub shaft Illa with respect to the turbine or machine shaft Ill.

Furthermore, as shown in Fig. 11, the servomotor apparatus, at 8|, and the valve 84 are arranged as an assembly capable of being handled as a unit, at |96, for attachment and detachment with respect to the valve housing ||J`I connected to the machine or turbine casing 91 in any suitable conventional manner (not shown). To this end, a structural member |98 has its inner end attached to the cover |99 of the valve housing and has its other end attached to the servo-motor cylinder 82. The unit, at |06, may be assembled with respect to the machine or turbine or removed therefrom by attachment of the ange |99 to the valve housing, the balanced valve Sli being readily removable with the unit. As shown, the valve includes spaced valve elements ||0 and III cooperating with valve seats formed on the anges H2 and H3 of the valve cage. The opening formed in the flange ||2 to provide the seat for the valve element IIU is of a diameter not less than the valve element I I so that the latter may be moved through the opening incident to removal and assembly of the unit.

Fig. 13, like Fig. 11, is provided with a load spring 18a; however, instead of the adjusting screw Ell being carried by the casing IIa, as in Fig. 11, the adjusting screw a is carried by'a support II 4 attached to the rotating governor head, at I3.

As shown in Figs. 6 and 12, the leaf spring I4 is preferably prebent with the result that it offers increasing tension force opposing straightening. With the direct form of governor, where increase in centrifugal force is accompanied by increase in transformed or governing pressure, no pressure exists in the transformed pressure space until the speed increases to enable the centrifugal force of the flyweights to overcome the tension of the leaf spring, the latter attaining a position such that it falls substantially within a rotational plane of the drive shaft, at the governing speed. The governing speed may be lowered by supplementing theicentrifugal force of the flyweights with force due to the spring 18, the greater the force of the spring 18 acting in a direction to increase the transformed pressure, the less the centrifugal force required to move the cup valve in a direction to increase the pressure.

On the other hand, With the inverse arrangement, a straight spring, or one which is not preset, as by bending, is used, the tension forceof such spring being zero in its normal operating position and the load spring balancing the force due to the centrifugal couple of the flyweights. As an increase in transformed pressure opens the motive fluid valve wider to increase the speed, the governing speed range is varied by adjusting theload spring, maximum speed occurring with maximum spring compression and the speed being reduced by reducing the compression.

As a speed governor operates in response to speed change to oppose change in speed, in the present arrangement, a change in centrifugal force is transformed into a change in liquid pressure, which is used to secure force amplification in the ratio of the relay pressure area to the pressure-responsive means pressure area. In both the direct and inverse arrangements, a change in speed brings about a change in motive fluid admission so as to oppose the speed change, the transformed pressure being increased with increase in speed to reduce the motive fluid admission, and vice versa, in the case of the direct arrangement, and being reduced with increase in speed to reduce the motive fluid admission, and vice versa, in case of the inverse arrangement.

In both the direct and inverse arrangements, as diagrammatically indicated in Figs. 14 and 15, the leaf spring lll takes up a position to place theiforces acting thereon in equilibrium, such forces being (l) Leaf spring tension force, t. f.

(2) Centrifugal force of flyweights, c. f.

(3) Pressure force of liquid acting on relay pressure area, p. f.

(4) Load spring force, s. f.

With the direct arrangement, equilibrium is attained with the centrifugal force and load spring force acting in a direction to increase the transformed pressure equal and opposed to liquid pressure force and leaf spring tension force tending to reduce such pressure. On the other hand, with the inverse arrangement, since the flyweiglits are cppositely arranged with respect to the fulcrum or bending portion of the leaf spring to give al centrifugal couple in the opposite direction, the centrifugal force is reversed as compared to the direct arrangement, that is, it acts in a direction to reduce the transformed pressure, so that equilibrium is attained with the load spring force tending to increase the transformed pressure being equal and opposed to centrifugal force, leaf spring tension force, and fluid pressure forcetending to reduce such pressure. Since increase in transformed pressure is used to reduce the admission of motive fluid in the direct arrangement, the effect of increasing the load spring for-ce is to bring about increase in trans formed pressure to reduce the speed. Therefore, with the leaf spring suitably preset, maximum governing speed occurs with the load spring adjusted for zero or minimum force and the governing speed is reduced by increasing the load spring force. On the contrary, Withthe inverse arrangement, since the centrifugal force acts in the oppostedirection and an increase in transformed pressure is used to increase the admission of motive uid to increase the speed, and Without any presetting of the leaf spring, an increase in load spring force has the effect of increasing the speed and Vice versa.

Prebending of the leaf spring is advantageous with the direct arrangement. With such arrangement, the leaf spring may be prebent t0 provide 'a tension force opposing straightening to secure a minimum transformed pressure for operation at the maximum governing speed, the load spring then being adjusted to its zero or minimum value, with the result that the load spring is adjustable to exert force from the zero or minimum value to a maximum value to reduce the governing speed correspondingly. On the other hand, with the inverse arrangement using a straight leaf spring or one which is not preset, the tension force of such spring is zero in its normal operating position; and,` with the load spring balancing the force due t0 the centrifugal couple of the iyweights, the load spring exerts iis maximum force for the maximum governing speed and such spring force is reduced by adjustment of the spring to reduce the governing speed.

While the invention has been shown in several forms, it will be obvious to those skilled in the art that it is not so limited, but is susceptible of various other changes and modifications without departing from the spirit thereof.

What is claimed is:

l. In governing apparatus for a prime mover pinze-vided with a rotary member, means providing a controlling liquid pressure space; means carried by and rotatable with the rotary member and including a valve movable axially of the member to vary the pressure in said space; and

a leaf spring and flyweight aggregate connected to the rotary member and abutting the valve; said aggregate including a leaf spring having inner and outer attachment portions joined by a flexible portion, means for connecting the outer attachment portion to the rotary member so that the leaf spring is disposed substantially in a ro- Jnational plane of the latter and intersects the axis thereof, and weight means connected to the inner attachment portion and arranged to respond to centrifugal force to cause the aggregate to exert thrust on the valve to effect change in space pressure dependent upon centrifugal force change, said weight means being comprised by a of Weights attached to opposite faces of the leaf spring and having their centers of gravity at diametrically opposite sides of the rotary member axis and spaced from opposite faces of the leaf spring with the centers of gravity arranged in a plane which intersects the flexible portion of the leaf spring lengthwise.

2. In governing apparatus for a prime mover provided with a rotary member, means providing a controlling liquid pressure space: means carried by the rotary member and including a valve movable axially of the member to vary the pressure in said space and having a pressure area subject to space pressure: a leaf spring and flywe'ight aggregate connected to the rotary member abutting the valve: said aggregate including a leaf spring having inner and outer attachment portions joined by a. flexible portion; means for connecting the outer attachment portion to the rotary member so that the leaf spring is disposed substantially in a rotational plane of the latter and intersects the axis thereof; and a pair of weights connected to the inner attachment portion of the leaf spring at opposite sides of the latter with the centers of gravity of the Weights at diametrically opposite sides of the rotary member, spaced from opposite faces of the leaf spring, and arranged in a plane intersecting the flexible portion of the leaf spring longitudinally so that centrifugal force acting on the Weights is effective to apply a centrifugal couple to the aggregate to cause the latter to exert thrust on the valve to effect change in space pressure dependent upon centrifugal force change: a load spring for exerting force on the aggregate to provide for space pressure dependent upon the loading of the load spring: and means for adjusting the load spring,

3. In a governor, means providing liquid under governing pressure and including a relay operable to vary the pressure: a drive shaft rotatable with apparatus whose speed is to be governed and provided with a head: said head including a ange connected to the drive shaft, a spacing member comprising end ring portions joined by an arcuately-extending portion to provide a clearance space, a ring member, and means for attaching one ring portion to the flange and for attaching the ring member to the other ring portion; and means for applying forces to the relay to operate the latter to provide governing pressure dependent upon rotational speed of the drive shaft and including an area formed on the relay and subject t liquid under governing pressure so that force is applied to the relay in a direction to effect reduction in governing liquid pressure and including apparatus for applying to the relay force which varies in response to rotational speed of the drive shaft and which cooperates with the liquid pressure force to operate the relay to vary the governing liquid pressure in response to rotational speed of the drive shaft: said apparatus including a leaf spring having inner and outer attachment portions joined by a flexible portion with the outer attachment portion connected to the head by being clamped between the ring member and the other ring portion so as to extend substantially in a rotational plane of the drive shaft and be engageable With said valve member to apply force tc the latter; a pair of Weights each. having a foot adapted to fit against one side of the leaf spring; and means for clamping together the feet of the Weights and the inner attachment portion of the leaf spring With the Weights disposed at opposite sides of the spring and with one of the weights located in the clearance space of said spacing member so as to leave the flexible portion of the leaf spring free for deflection; said Weights having their centers of gravity at diametrically opposite sides of the drive shaft axis, spaced from opposite faces of the leaf spring, and in a drive shaft axial plane intersecting said exible portion in the direction of its length to provide for the weights being statically balanced with respect to the drive shaft and for the development of a couple due to cenn trifugal force of the weights tending to deflect the leaf springr laterally to apply force to the valve member dependent upon speed of the drive shaft.

4. In a governor, means providing a space for liquid under governing pressure; a drive shaft rotatable with apparatus Whose speed is to be governed and having an axial bore forming a portion of said space and said bore opening through one of drive shaft to provide a discharge port; a plunger coaxial with the drive shaft; means connected to rotate with the drive shaft and guiding the plunger for axial movement; a

cup valve carried by one end of the plunger and arranged in covering relation with respect to said discharge port to control the escape of liquid from the latter and presenting an area subject to space pressure so that force dependent upon the latter is `applied to the cup valve in a direction to open the latter to lower the space pressure; a leaf spring having inner and outer attachment portions joined by a flexible portion; means for connecting the outer attachment portion to the drive shaft so that the leaf spring extends substantially in a rotational plane of the latter and intersects the axis of rotation thereof; a pair of Weights; and means for attaching the weights to opposite sides of the inner attachment portion of the leaf spring with the centers of gravity thereof arranged at diametrically opposite sides of the drive shaft axis, spaced from opposite faces of the leaf spring, and having their drive Shaft axial plane intersecting the flexible portion lengthwise to provide for a statically-balanced relation of the Weights with respect to the drive shaft axis and for the development of a couple tending to deflect the leaf spring laterally to apply force to the plunger dependent upon speed of the drive shaft.

5. Apparatus as claimed in claim 4 with a load spring exerting force on the plunger to act on the cup valve to provide governing pressure dependent on the force and means for adjusting the load spring to vary the force applied thereby to the plunger to vary the governing liquid pressure in order to adjust the governing speed over a suitable range.

6. In a governor, means providing a space for liquid under governing pressure; a drive shaft rotatable with apparatus Whose speed is to be governed and having an axial bore forming a portion of said space and said bore opening through one end of the drive shaft to provide a discharge port; a plunger coaxial with the drive shaft; means carried by the rotary member and guiding the plunger for movement axially of such member; a cup valve carried by one end of the plunger and arranged in covering relation With respect to the discharge port to control the escape of liquid from the latter and presenting an area subject to space pressure so that force dependent upon such pressure is applied to the cup valve tending to move the latter in an opening direction to lower the space pressure; and means for applying force to the plunger in opposition to said opening force and including a leaf spring having inner and outer attachment portions joined by a exible portion, means for connecting the outer attachment portion to the drive shaft so that the leaf spring extends substantially in a rotational plane of the drive shaft, a pair of Weights, means for attaching the Weights to the inner attachment portion at opposite sides of the leaf spring with the centers of gravity of the Weights disposed at opposite sides of the drive shaft axis, spaced from opposite faces of the leaf spring, and in a drive shaft axial plane intersecting the leaf spring longitudinally to provide for a statically-balanced condition of the Weights and for the development of a couple tending to deflect the leaf spring laterally to apply force to the plunger in opposition to the liquid pressure force applied thereto.

7. In a speed governor for a machine having a rotary element, controlling means for the machine and including a force-responsive member and a leaf spring and Weight aggregate abutting the member to apply force thereto; said aggregate including a leaf spring having inner and 1 l outerl attachment portions joined by a exible portion, means for connecting the outer attachment portion to the rotary element so that the leaf spring extends substantially in a, rotational plane of the latter and intersects the axis of rotation thereof, and a pair of weights connected together and to the inner attachment portion of the `leaf spring, said weights extending in opposite directions from the rotary element axis and havin'gtheir centers of gravity spaced from opposite faces' ofthe leaf spring and in an axial plane of the Yrotary element so that the centrifugal force of one Weight may balance that of the other excpt for the centrifugal couple of the Weights applieclto the leaf spring to cause the aggregate 15 to exert force on said member.

ANTHONY F. SCHWENDNER.

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

UNITED STATES PATENTS Number Name Date 1,334,902 Howe Mar. 23, 1920 2,080,243 Warner May 1l, 1937 2,239,602 Gottlieb Apr. 22, 1941 2,247,434 Bryant July 1, 1941 2,323,664 Kindleman July 6, 1943