US2239602A - Governing apparatus - Google Patents

Description

April 22, 1941.- M. GOTTLIEB GOVERNING APPARATUS 4 Shees-$heet s Filed June 28, 1939 IHHI INVENTOR m. 72;, M ATTORNEY Mnmous Gar-ruse.

April 22,1941. V GOTTLIEB v Q 2,239,602

GOVERNING APPARATUS Filed June 28, 1939 4 Shets-Sheet 4 Fla] INVENTOR W. V; M

ATTORNEY Mrmipus GOTTLIEB.

turbine, and it hasfo'r'an turbines. it is necessary,

' ness of the vwelt of P per by variati 'steamused tion to constancy of speed for given conditions that operation of the turbine pensation for variations in speed, over the relatively wide range, the per- 50 Parents-alps. 2r, 194i [PATENT I OFFICE v fiazs'acozQ covnanmc arraaarus Malliolls Gottlieb,

Westinghouse Electric pm, East Pittsburgh, la.,

Pennsylvania Philadelphia; rs; assignor to aluminium com a corporation of o ap ncsubsrue 28,1939,SeriflNo.281,595

lSClaims'.

M'v invention relates; to a governing mechanism fora primemover,

object toprovide apparatus ofthis character capable of adjustment to secure operation of the turbine or prime mover over a wide speed range. v 1

In certainfindustrial applications ofsteam whichadiustment has, been made shall be maintained irrespective of changes in load. application-is to depends upon a num-' ber of factorsincluding. speed of the driving turbine. -Accordingly. if the speed is adjusted for a certain paper web tummy! is necessary tomaintain the speed forheating the' mill rolls. In addi" with load variations, conditions may vary so over a wide range is necessary. Therefore,

provide a governing m adjustable. to give a wide speed range andwherein each speed s is maintained substantially constant irrespective- "of load variations.

- A-further object of my vide a pressure transformer gov-.1 Y ernor and the admission valve of; a prime-mover and wherein the movable or controlling part of the transformer may have relatively large clearance to minimize friction-andwhereln. di flicul-r 35 ties on.account ofmechanical interference and hydraulic reaction are avoided.

A further object of my invention. is io provide a governing m including a pressure transformer capable ofogidving speed com- A further object of my invention is. to provide a pressure transformer between a centrifugal governor and-the admission valveof a prime mover and capable,'not only of giving speed compensations for variations in load, but also, speed compensain scale effect of the centrifugal governor centage of regulation or speed variation from no loadto full load may be maintained at a minifor example, a steam not only that speed adiustment be provided for, but that the speed for If the drive a paper mill, thejthickincreased degree of speed compensation; substantially con of load variations ns in'the. requirement for PM a further.and.--- more particular object ofmy invention is'to- 25,ha I

sienna-as w b i- "a wherein :the transformer is 4 ing description and claims taken inconnection with the accompan ldrawings forming a part of this application, in which:

Fig. 1, is a sectional view showing a turbine with the improved governing mechanism applied thereto; v 7

Fig. 2 is an enlarged sectional view showing the centrifugal governor and Fig. 1,

a second embodiment; FigAisaview siinilar a fourth embodiment;

Fig. 5 13a view similar to Fig. 2 but showing a third embodiment having means to secure an to Fig. 2 but showing 5a is a diagram illustrative of principles of-operationof the Fix. 6 illustrates I ,angenient shownin Fig. 3; and, frshows arnrodifled used with, the governing apparatus of Figs. 1

: -In Fig. 1, there is an admission valve ll controlled by a servo motor, at It, which operates in response to transformed governor, at II. a.

0' The turbine, at II, has, at one end thereof, the vertical casing I with the vertical governor structure and. operation of the transformer.

The centrifugal governor,. at l5, includes a drum construction 24 provided with a transversely extending leaf thereon tends to produce movement thereof with deflectionfof the leaf spring. The leaf spring has .a bent or inverted. U-shaped portion 21 has. cylinder 3 0 comprising bore portions 32,

transformer of- F18. 351. a view similar, to Fig. 2 but showin embodiment shown in Fig. 5;

a modified form of the arform; of servo-motor shown a steam turbine, at Il oil pressure furnished by thetransformer, at ll, controlled by the centrifugal projecting flange 23, it also contributes to the spring 25 having its ends 5 attached to the drum. 'Flyweights 26 are attached tolthe leaf spring andcentrifugai force acting I 33, and 34 of smaller diameter than the intermediate bore portions 35 and 35. The upper end of the cylinder is closed by a plug 3|. A tubular plug 31 has a close sliding fit within the upper bore portion, the intermediate bore the body 29 to the lower bore or chamber 34 for action on the annular piston area 59. 7 With the form of the invention shown in Figs. 1

and 2. assuming a decrease in load, the speed portion 33 provides a guide for the piston or plunger portion 39'of the transformer relay 39,

48 formed in the body 29 and communicating ing, respectively, with ports or passages 41 andwith thecylinder between the plugs 3| and 31. Oil, or other appropriate liquid, is supplied under suitable pressure by the conduit 50 through the registering passages 45 and 41 to the cylinder 30, the port or passage 41 being provided with the metering orifice 5|. The registering passages 49 and 45 are connectedto the conduit 52, leading to the pressure responsive servo-motor, at l2.

The relay 39 has a cup 54 formed at its upper. end, the cup being in covering relation with respect to the lower or discharge end of the plug bore and having a sharp annular edge 55 defining, with the radial face or seat 44, a radiallydisposed annular escape orifice, whose flow area is restricted by upward movementof the element 39 and vice versa.

relay would increase, causing the bent portion 21 of theleaf spring to move the relay 39 upwardly to decrease the flow area of the annular orifice. thereby increasing the transformed oil pressure,

and this operation continues until the downf wardly-acting force of the transformed oil pressure acting on the piston area provided by the cup valve balances the increase in centrifugal force." The increase in transformed oil pressure is not applied immediately to the lower chamber or bore for action' on the piston area 59 but in a delayed manner due to the restricted rate of flow permitted by the adjustable orifice 59. As,

the pressure gradually increases in the lower bore o rchamber, 35 it acts on the piston area 53 to cause further decrease in the annular orifice and increase in the transformed oil pressure, such further increase in transformed oil pressure bringing about further restriction of opening of the admission valve to minimize speed change due to load'change so that the speed may be restored substantially to the same value it had before Thus, there isan enclosed space, provided by,

the bore 43,-the upper portion of the cylinder 30, the passages 49, and 52, and the pressure chamber 56 of the servo-motor, to which liquid is supplied by means of the metering orifice 5| and from which'liquid escapes by means of the annular escape orifice. Therefore, the pressure existing in such space depends upon the flow area of the annular escape orifice, the pressure increasing with decrease in flow area and vice versa; and, as the flow area of the annular escape orifice is determined by the relay 39, it will be apparent that movement of the relay secures a transformed oil pressure in the space.

The relay 39 is' moved the very slight amount required to vary the transformed oil pressure by the opposing forces due to centrifugal force of the fiyweights and to transformed oil pressure acting on the piston area provided by the cup valve 54, the centrifugal force of the fiyweights being opposed by the deflection resistance of the leaf spring 26. v

-The relay 39 is preferably provided with .a downwardly-facing annular piston area 59 exposed to the pressure existing in the enlargement or chamber 35. The piston area of the cup valve 54 is preferably made somewhat larger than the annular piston area 53 so that, with transformed oil pressure supplied to the chamber 35,

a suflicient downwardly-acting differential pressure force will be effective to keep the relay stem 4| in contact relation with respect to the U- shaped spring portion 21.

Preferably, oil under transformed pressure is supplied from the passage 45 through an adjustable orifice 53 to the air bell or chamber in the upper portion of the cover 22, and, from the latter, oil passes through the bore 9| formed in the load change. vOn the other hand, an increase in primemover load is followed by contrary operation, the delayed effect of change in transformed oil pressure assuring of opening of the admission valve sufficiently to effect substantial speed correction with increase in load.

While the extent of speed correction or compensation depends on keeping the differential piston effect at a minimum for maintaining the relay stem 4| in contact relation with, respect to the leaf spring, the extent of compensation as well as securing a desired differential effect for I the purpose indicated is assured by having the til, with the needle valve 54 entirely closed, it is pressure chamber 39 communicate with the drain passage 53 by means of a needle valve 54. If the needle valve 64 is wide open, then there can be no accumulation of pressure in the chamber 35 with the result that the piston area 59 would be ineffective and the downwardly-acting transformed oil pressure would be opposed entirely by the centrifugal force effect of the flyweightsh On the other hand, as the valve 54 restricts more and more escape from'the chamber 35, the higher will be the maximum pressure in the latter, un-

possible to provide for transformed oil pressure in the chamber 35.

As the relay 39 does not have to control pressure and exhaust ports, it merely having a cup valve 54 in covering ,relationwith respect to the discharge opening 43 to define the annular escape orifice and the chamber provided by the bore 35 to which said orifice discharges being connectedto the drain passage 53, it will be ap parent that the relay may have large clearances with respect to cooperating'parts with the result that it may move freely and in a substantially frictionless manner. Furthermore, any chance of binding or of mechanical interference of closely fitting parts is avoided and there are no sharp edges, andport corners to wear and'impair accuracy of operation. Also, as the annular escape orifice provided between the thin edge 55 of the cup valve and the seat 44 is directed radially, there is no axial component of hydraulic reaction present and tending to introduce a variation or error in the operation of the governor.

Speed adjustment of the form of the governing apparatus shown in Figs. 1, 2, and 7 is secured mg the slot be increased and vice versa,

this adjustment, the governor control the admission rection, depending change; and movement of the operating piston the upper end ofthe bore 32a adjacent to the 75 aasacos by varying the position of the plug 31 in the bore,

'fl, the plug being raised and lowered. for exportion OI engagample, by means of the crank it formed in the plug 31, the crank portion being carried by a stub shaft 1 turned by means of worm gearing, at l8,'operated by a speed changer shaft N. If the plug 31 is raised, it will be apparent that the operating speed will that is, by means of is rendered capable of operating er a wide range of operating speeds and functioning at each operating speed to provide for governing of the turbine from. no load to full load. v

The oil under transformed pressure is supplied by the conduit "to the enclosed pressure chamber 56 of the servo-motor, at If, the pressure chamber being preferably defined by a movable abutment 66a, inner and outer bellows elements 61a and 68a, and the body structure a of the servo-motor. pilot valve and operating cylinders 'II and 12 a pilot valve 13 being arranged in the pilot valve cylinder and an operating piston 14 being located in the operating cylinder 12. The pilot valve ll has suitable lands, as illustrated, for controlling admission and exhaust ports for securing the admission and exhaust of motive fluid to" opposite ends of the operating cylinder 12 to effect movement of the operating piston ll. A spring I! exerts its force on the upper end of the pilot valve to keep the lower end-thereof in contact relation with respect to the movable abutment a.

The operating piston 14 has a stem 11 connected to the admission valve II and the stem is pivoted at the intermediate point .18 of a lever It, oneend of the latter being pivoted, at ll, to the body structure as, and the other end being" connected to the rod 8! attached to the lower end of the spiral spring .2; the upper end of the latter being attached, by means of the. rod 83 to the movable abutment a. I

This follow-up mechanism provides for changing the force of theyspring if to compensate for change in transformed oil pressure in the chamber it so as to restore the pilot valve to neutral position. In other words, assuming a change in load, the transformed oil pressure changes with the result that the pilot valve II is moved to and exhaust of motive fluid to the operating cylinder 12 so as to move the admission valve Ii in an opening or closing diupon the direction of load will continue until the I4 and of the valve. li

82 effected by such change in force of the spring movement compensates for the change in force" of fluid pressure acting on the abutment "a, whereby the latter is restored to a position such that the pilot valve II is brought to neutral or cut-off position, whereupon movement of the operating piston and of the admission valve ceases and the steam admission flow area of the latter remains flxed until the load again changes.

In Fig. 3, there is shown a second embodiment of the invention to that already tion to the leaf spring 28, the governor includes a loadspring 85 and a modifledform of speed changer, these diflerences necessitating a differ- The body a flange 06 attached to the supp y pas a es ,threade'd connection closure plug Ila. The hollow plug l'la has upper metering orifices Bic connected tothe pressure "a, a, and Stand lower ports .1 connected tothe passages a, a, and If.

The depending body 29a has an external changer nut 80a having external worm teeth 09 opposed by the leaf springs! and by The servo-motor body structure; includes the usual of the transformed oil pressure b with respect to the drain passage and which is similar, in general, described except that, in addimeshing with the worm shaft ii. The lower end of the speed changer nut it engages a roller thrust bearing 92, which, in turn, engages the follower 93 forthe upper end of the load spring II. The lower end of the load spring engages a follower or abutment l4 whichhas a thrust connection with respect to the bent portion 21 of the leaf-spring 26. Thus, not only is the centrifugal effect of the flyweights spring 85, but-the force of the varied to varythe speed setting by operation of the speed changer shaft ii, an increase in speed setting being secured by increase in force of the load spring and vice versa.

In the forms the arrangement is such that, with an-increase in speed, the relay 3! is moved upwardly slightly-to increase the transformed oil pressure, that is, a decrease in load calls for an increased transformed oil pressure and vice versa. The inven tion v may be arranged to secure the opposite relation, that is, with a decrease in load, instead increasing, it de creases. Accordingly, in Fig. 4, there is shown an embodiment which is similar to Fig. 3 except that the transformer is reversed. In this modiflcation, the dependingbody 28b is provided with a plug 31b at the lower, instead of the upper, end thereof, and the plug has a central bore 43b whose upper escape end radial seat. b with which cooperates the inverted cup 54b of the relay 39b. As before, oil from a suitable source is suppliedthrough a metering oriflce Blbto the bore 43b and the latter is connected by means of passages 48b and b to the pipe or conduit leading to the servomotor, The intermediate or drain chamber lib receiving oil escaping from the radially directed annular oriflce is connected to the drain pas- 838a lib.

The cover chamber lib connected, 'by means of the adjustable oriflce 59b, to the transformedoil pressure space including the passages'ltb and band bell ,is connected by the bore 43b, and the air means of a passage lb to the b to which is exposed the piston area be! the relay 39b. The chamber 38b preferably has valved communication pressure chamber spring 98 preferably exerts its force on the upper end of therelay, which force, together with that of the fluid pressure acting on the upwardlyfacing piston area 58b, acts in opposition to the fluid pressure force acting on the piston area of the cup valve 54b to keep the stem lib in contact relation with respect to the bent portion 21 of the leaf spring.

With the form of invention shown in Fig. 4, the principle of operation is substantially the same as that described in connection with Fig. 3 f

except that, instead of the transformed oil pressure increasing with a decrease in load and vice versa, such pressure decreases and vice versa.

While the governing arrangements so far described are capable of governing over a relatively wide speed range with a reasonably small speed 88 with respect to the speed 90 on the speed changer the load latter may be of the invention so far described.

is bounded by a 22b is providedwith anair bell or upwardly-facing change from no load to full load at each operating speed, nevertheless, there is a droop or increased percentage of speed change, from no load to full load as the operating speed is lowered. For example, referring to diagrammatic Fig. 5a, and comparing the speed change from no load to full load to secure the desired transformed oil pressure change, for example, 40 .pounds at no load to pounds at full load, if, at a speed setting of 6.000 R. P. M., the percentage of regulation is .02 percent from no load to full load, then, at the setting of-1000 R. P. M., the speed change from no load to full load may be of the order of 7% percent. Thus, there is a a relatively greater speed droop at the lower end of the speed range than at the'higher end thereof. This is due to: v v

(a) The differential area of the transformer .relay is limited to eifect a small downward force so that the relay will, at all times, maintain contact with the flyball element. Now, since the transformed oil pressure, which varies with the turbine load, acts on this difierential area, it will be obvious that the netdownward force also varies with the transformed oil pressure. Therefore, there is a slight change in speed caused by; the change in transformed oil pressure.

('b) In any type of relay, some travel, how-. ever s'mall,-- is necessary to produce a change in .flow across its control edge or escape orifice;

and, since the system is not scaleless, a slight change in speed is needed to produce this relative travel.

Since the force necessary to obtain a given change in transformed oil pressure is thesame regardless of the operating speed'and since the available power of the speed responsive element varies with the scale of the spring, it is evident that, at the lower speeds, a relatively larger percentage of speed change is needed to cause a change in transformed oil pressure than is required for such a change at higher speeds, this being obvious from Fig. 5a,wherein it will be seen that, if the speed setting is decreased, the percentage of speed change. from no load to full 7 load increases.

r In Figs. 5 and 6, there are shown means for compensating for the aforementioned causes of speed droop. Absolute speed compensation is accomplished, without any added friction, by providing a definite downward force on the transformer relay 300 by means of a small piston, in Fig. 5, and by means of a spring, in Fig. 6. Now, since there is a definite downward forceon the transformer relay which will prevent the relay leaving contact with the flyball element, the dif- 2,239,002 7 reverse is true in Fig. 5, the piston area 000 being sufliciently larger than the piston area of the cup valve 540 to secure an upward differential piston force to compensate for the change in scale eflect of the governing spring means. This relationship of piston areas necessitates the employment of other means to keep the relay stem 4Ic in contact relation with respect to the fiyball mecha-' nism. Accordingly, the relay carries a piston I00 arrang d to be acted upon by fluid pressure so as to exert a downward force on the relay sufiicient to maintain the contact relation.

The introduction of the piston I00 calls for changes in detail of the fluid pressure passages of Fig." 5, as compared to Fig. 3. Instead of the pressure supply passage 01a communicating through orifices 5Ia with the plug bore 43a, as

in Fig. 3, the pressure supply passage 41c has a vertical end portion alinedand communicating with the plug bore He, the plug 310 having lower openings 01c communicating with the transformed oil pressure passage 460; The metering .orifice for supplying oil to the transformed oil pressure space is comprised by the annular area 5Ic between the periphery of the piston I00'and the interior of the bore liq-and the pressure difference across this orifice provides the downwardly-acting force to keep the relay in contact relation with respect to the fiyweight mechanism.

In Fig. 6, the arrangement is similar to Fig. 3 so far as the metering orifice 5Id is concerned and the'relationship of piston areas d and 50d is the same as that described in connection with Fig. 5. As the piston area 50d is made sufiiciently larger than the piston area of the cup valve 54d to compensate for change in scale of the governor spring means, as in Fig. 5, it is necessary to employmeans for maintaining contact relation of the relay 00d with the fiyweight mechanism. Accordingly,- a spring IOI is arranged within the plug borefld and has its lower end bearing on the relay 00d to maintain the contact relation.

Fig. 'IshoWs a transformer and servo-motor arrangement which is similar in principle to that of Fig. 1 except that, byhaving the servo-motor pilot valve 'alined with the transformer some simplification of structure and arrangement of fluid passages is provided. The bore lie of the plug 31c has its upper end in communication with the .piiot valve, cylinder I02 constituting an up-' .ward extension of the body Me. A servo-motor pilotvalve I03 fits the cylinder and it controls communication of the pressure and exhaust ports ferential area of the relay can now be made so that. an increase in transformed oil pressure causes an upward force on the relay corresponding to the force needed to movethe relay to its new position, thus establishing equilibrium at a need of speed change at any operating speed. In other words, the upwardly-acting 'difierential pressure force may be sufilcient to compensate for the scale effect of the spring so that,

for a wide range of operating speeds and at each different transformed oil pressure without the.

rangements are similar to Fig. 3 except that, in-

stead of the piston area of the cup valve 54 being larger than the piston area 50, as in Fig. 3, the

I04 and I05 with passages I01 leading to opposite ends of the operating cylinder I 00 having an operating piston I00 therein. The pilot valve I00 is made hollow for a substantial portion of its length, is openat the bottom, and it carries an axially-arranged stem III. The lower end of the stem engages an abutment III forthe upper end of the spiral spring III, the lower end of the latter being supported by the body structure 20c,

Follow-up mechanism associated with the operating piston rod III and including spring means cooperates with the upper end of the stem As shown, such follow-up mechanism includes a lever Ill having one end pivotally connected at III to the rod III, being fulcrumed at an intermediate point H6, and having its other I Liquid is admitted to the, hollow interior of the pilot valve I03 and to the lower portion of.

the cylinder I02 by means of one or more metering orifice .ports He provided in the pilot valve and in communication with the high pressure port It. The space included within the hollow pilot valve, within the lower portion of the cylinder I02 and in the bore He, therefore, constitutes the transformed oil pressure space to which 011 is admitted by the metering orifice He and out departing from the'spirit thereof, and I desire, therefore, that only such limitations shall beplaced thereupon as are specifically set forth from which oil escapes by means of the radiallydirected annular orifice defined between the cup v lve 54c. and the lower end e of the plug He. The lower end of the cylinder I02 is connected /by a passage I24 with the space its to which is directly exposed the downwardly-facing ,piston area 58a, of .the relay tie, the passage l2! including an adjustable orifice 125. {An air bell I28 communicates withthe chamber "6, the passages affording this communication being assoin the appended claims.

What I claim is:

1. In governing apparatus, apressure-responsive device; means for developing force which varies as a function of speed; spring means; a thust member acted on by the resultant of forces of said first means and of the spring means;

speed-changing means; means including said pressure-responsive device for providing a space for fluid under pressure; said last-named means ciated with the drain passage tie for the drain space or: chamber c and a valve 64c controls communication of the drain passage to any desired extent with-the chamber 36c. It will, therefore, be apparent that the passage III, the adiustable orifice-I25, and the air bell constitute an accumulator orirnpedance means, which, as before, provides for delayed application of trans- H formed pressure in the chamber 38c. If the valire e is closed, then the maximum pressure accumulating inthe chamber tie is the transformed oil pressure, but the maximum may be less to any having an escape port; a member in thrust-transmitting relation with respect to the thrust member and having covering relation with respect to said escape port to define an escape orifice; means for supplyingfluid to said space so that variation in-the escape orifice provides for variation in fluid pressure in the space; flrst compensating means responsive to fluid pressure changes in said space due'to temporary speed changes incident to load changes to effect speed compensation with change in load; said flrst compensating means includinga piston area formed on said member in opposed relation to the piston areaprovided by the portion thereof subject to space pressure at the escape orifice, means providing a chamber for the first piston area, and means providing for desired extent depending upon the adjustment of the valveile. Y I I Erom' the structure described, it will be apparent that the governing and transformer apparatus of Figure 'I is identical in principle to that shown in Figures 1 and 2. Instead of having the metering orifices associated with'rthe hollow plug 31 and providing'a separate pressure chamber 56 for the servo-motor pilot valve, as shown in Figure 1, in thisview, the pilot valve'aligned lagging relation of change in pressure in aid chamber relative to that in said s'pace; and 0- end compensating means for effecting speed co pensation incident to speed adjustment of the governor, wherebyv said governing system may govern the prime mover over a wide speed range v with minimized speed variations at each speed with the transformer is constructedand arranged to provide both the metering, orifices and to function as its own pressure responsive device,

Transformed oil pressure-provided in the lower portion of the cylinder I02 provides an upward force acting on the pilot valve. In addition to this force, the pilot valve is also acted upon by the force of the springs H2 and 12.. Assuming that the pilot valve [II is in neutral-cut-oif position and that a change in transformed oil pressure occurs due' to a change in load, then the effect thereof is to upset the equilibrium condi-. tion of forces for neutral pflot valve position with the result that the latter is moved, thereby bringing about connection of the passages III with the pressure and exhaust ports I and I" so that motive fluid is admitted and exhausted to the operating cylinder I to move the operat-.

ing piston. The operating piston I09 moves in consequence to adjust thesteam admission valve and this movement is transmitted through the foHoW pp mechanism to change the force of the springlll, the follow-up movement continuing until the force of the latter spring is changed sufilciently to compensate for the change in force setting from no load to full load; said second compensating means including a disc carried by said member and arranged in a cylindrical bore providing said escape port, the disc dividing the bore into a portion forming a part of said pressure space and a portion providing a fluid-pressure supply space and cooperating with the wall-i of the bore to provide an orifice afiording com-1 f munication of the supply space with said pressure space, the pressurev of fluid in the supply space acting on the disc to exert a force. on said' member to keep the latter in thrust-transmitting relation with respect to the thrust member so that said piston areas )may have a differential action sufilcient to provide for'force exerted on the member toscompensate for the spring scale.

incident to speed adjustment over the wide speed range.

2. In governing apparatus, a pressure-responsive device; means for developing force which varies as a function of, speed; spring means; a

thrust member, acted on by the resultant of forces of said flrstmeans and of the spring means; speed changing means; means including said pressure-responsive device for providing a space for fluid under pressure; said last-named means havin an escape port boundedby a surface extending transversely of the latter, a. member in thrust-transmitting relation with respect to the thrust member and having covering relation with respect to said port and cooperating with said surface to define a radially-directed circular escape orifice; means for supplying fluid to said space so'that variation in; the escape orifice provides for variation in the fluid pressure inthe space; first compensating means responsive-to fluid pressure changes in said space and due to temporary speed changes inciden to load changes to eifect speed compensation with hange in load? said first I sure to said space; a mem formed on said member in opposed relation to the piston area provided by the portion thereof subject to space pressure at the escape orifice, means providing a chamber for the first piston area, and means including a passage connecting the pressure spaceand said chamber and providing for lagging relation of pressure changes in said chamber relative to said space; and second compensating means for effecting speed compensation incident to speed adjustment of the governor, whereby said governing system may governthe prime mover over a wide speedrange with minimized speed variations at'each speed setting from no load to full load; said second compensating means including a device for exerting force on said member in a direction to maintain the latter in thrust-transmitting relation with respect to the thrust member so that said first piston area may be made sufficiently larger than the piston area of the member bounded by the annular orifice to exert force on said member compensating for changes in transformed fluid pressure and changes in spring scale.

3. In governing apparatus, a pressure-responsive device; means for developing force which varies as a function of speed; spring means; a

thrust member acted on by the .resultant of forces of said first means and of the spring means; speed-changing means; means including said pressure-responsive device for providing a space for fluid under pressure; said last-named means having an escape portbounded by a surface extending transversely,the'reof; means including an orifice for supplying fluid under presr in thrust-transmitting relation with respect to said thrust member and in covering relation with respect to said escape port and cooperating with saidv surface to define a radially-directed circular escape orifice; first compensating means responsive to fluid pressure changes in said space and due to temporary speed changes incident to load changes to effect speed compensation with change in load; said first compensating means including a piston area formed on said member in opposed relation to the piston area provided by the portion of the member subject to space compensating means including a piston area surface extending transversely thereof; a member in thrust-transmitting relation with respect to the thrust member and provided with a cuphaving an annular sharp edge cooperating with said fiat surface to define a radially-directed circular orifice; first compensating means responsive to fluid pressure changes in said space and due to temporary speed changes incident to load changes to eflect speed compensation .with change in load; said first compensating means including a piston area formed on said member in opposed relation to the piston area provided by the cup and bounded by the annular orifice, means providing a chamber for the first piston area, means providing a-passage affording I communication between the pressure space and pressure and bounded by the annular orifice,

ber relative to the space; and second compeir fili sating means including a device for applying force to said member to maintainthe latter in thrust-transmitting relation with the thrust member and to compensate for changes in scale of said spring means incident to speed adiustment of the governor effected by operation of the speed-changing means, whereby said governing system may govern the prime mover over a wide s eed range with minimized speed variations at each speed setting from no load to full load.

4. In governing apparatus. a pressure-responsive device; means for developing force which variesas a function of speed; spring means; a thrust member acted on by the resultant of forces of said firstmeans and of the spring means; speed-changing means; means including said pressure-responsive device for pioviding'a space for fluid under pressure; means including an orifice for supplying fiuid to said space; said lastnamed means having an escape port bounded by a said chamber and including an air bell, and means providing an orifice in saidpassage between the air bell and the pressure space; and second compensating means for effecting speed compensation incident to speed setting adjustment of the governor, whereby said governing system may govern the prime mover over a wide speed range with minimized speedvvariations at each speed setting from no load to full load; said second compensating means including a device acting on the member to maintain the thrusttransmitting relation thereof with respect to the thrust member in order that said piston area may have such a differential relation as to exert force on the member to compensate for changes in scale effect of said spring means.

5. In governing apparatus, a pressure-respom sive device; means for developing force which varies as a function of speed; spring means;-

a thrust member acted why the resultant of forces of said first means and of the spring means; speed changing means; means including said pressure-responsive device for providing a space for fiuid under pressure; said last-named means having an escape port for the pressure space; a member in thrust-transmitting relation with respect to the thrust member and in covering relation with respect to said port to define a circular escape orifice bounding a first fice provides for variation in fluid pressure in,

the space; said member having a second piston area arranged in opposed relation to the first area; means providing for. application of fluid pressure from said space to said second piston area; and biasing 'means for maintaining said member in thrust-transmitting relation with respect to the thrust member in order that the second piston area may be made sufliciently larger than the first to compensate for the scale of said spring means incident to speed adjustment. I

6. In governing apparatus, a pressure-responsive device; means for developing force which varies as a. function of speed; spring means; a thrust member acted on by the resultant of the forces of said first means andofthespringmeans; speed-changing means; a pressure transformer providing transformed fluid pressure for action on the pressure-responsive device; said transformer including a con-trolmember in contact relation with respect to said thrust member and serving to secure changes of transformed fluid pressure in predetermined relation with respect to governing force changes; means responsive to transformed fluid pressure changes due to temload; and means providing for the application of transformed pressure to th control member to secure modification of the transformed pressure to compensate for changes in scale of said spring means incident to adjustment of the speedchanging means over a wide speed range in order to minimize speed variations at each speed setting from no load to full load.

. 7. In governing apparatus, a pressure-responsive device; a centrifugal governor including flyq weights, spring means, and a thrust member acted on by opposing effects of the flyweights and of the spring means; a pressure transformer providing transformed fluid pressure for acting on the pressure-responsive device; said transformer including means providing an enclosed transformed fiuid-pressure space in communication with the pressure-responsive means and provided with an escape port bounded by a surface extending transversely of the latter and a member arranged in covering relation with respect to the port and cooperating with said surface to define a radially-directed circular escape orifice and in thrust-transmitting relation with respect to said thrust member; compensating means responsive totransformed fluid pressure changes due to temporary speed changes incident to load changes to eflect speed compensation with change in load; said compensating means in;

cluding apiston area formed on said member in opposed relation to the. piston area thereof bounded by the annular-orifice, means providing a chamber'for the first area, and means includrelation with 'respect'to exitendo to provide a radiallyected annular escape oriflee, and having a pi n'portion.flttingsaid cylinder, the portion of said cylinder between one end of the p ston portion andsaidport 'providing a drain s ace for the annular orifice and the portion of the cylinder extending beyond the of the speed setting; means including saidpres ing a passage between the transformed fluid- 1 pressure space and said chamber and providingfor lagging relation of pressure changes in said chamber relative to the transformed space. I

'8. In governing apparatus, a pressure-responsive device; a centrifugal governor including flyweights, spring means, and a thrust member act pressure ed on by opposing effects of the flyweights and of the spring means; a pressure transformer providing transformed fluid pressure foracting on the pressure-responsiveHevice; said transformer including means providing an enclosed transformed fluid-pressure space in communication with the pressure-responsive means and provided with an escape port bounded by a flat surface extending normally with respect thereto,

means including an orifice for supplying fluid under pressure to said space, a member in thrusttransmitting relation with respect to said thrust.

member, and acup carried by the member and having a thin annular edge cooperating with said flat surface to provide a radially-directed circular escape orifice; and compensating means responsive to transformed fluid pressure changes due to temporary speed changes incident to load changes to' effect speed compensation with change in load.

9. In governing apparatus, a pressure-responsive device; a cylinder; means providing an enclosed space in communication with said pressure-responsive device and having an escape port opening into one end of the cylinder and axially aiined with the latter; said means having a surface bounding the exit end of the port'and ex- 7 tending transversely with respect to the axis of the latter; means including an orifice for supplying pressure fiuid to said space; speed responsive means operated by the prime mover and having a thrust member aiined with the axis of said cylinder; an elongated. member having a s stem at one end in abutting relation with respect to said thrust member, having acupin covering sure-responsive means and providing aspace for I liquid under pressure; said last-named means having a discharge port for said 'space;',fa.;meni- I her in thrust-transmitting relation with respect" to said thrust memberand-cooperating port to define an escape orifice; means'for-su'pplying liquid to said space sothat the pressure 1 therein is a function of the flow area of. ,'the escape orifice; means for maintaining said meme I her in thrust-transmitting relation with-respect 'to the thrust member; and means including the'i abutment area of the portion of said member' at' the orifice subject to'pressure of said space and an opposing piston area subject to said pressure to pmvide adiii'erential' efi'ect compensating for the change in spring scaleincident to change in speed setting.

11. In governing apparatus, apressureresponsive device; means providing an enclosed's'pace in communication with said pressure-responsive device and having an escape port whose-discharge end is bounded by a fiat sin-face; means includ ing-an orifice forjsupplying'pressure fiuid to said 1 space; speed responsive means operated by the J prime mover and having a thrust member; means providing a guide aiined longitudinally with said port and thrust member; andan elongated member having a stem at one endin abutting relation with respect to said thrust member, having a cup in covering relation with respect-to the exit end or said port and cooperating 'with said flat boundary surface to provide a radially-directed annular escape orifice, and having a slide-portion fitting said guide.

12. In governing apparatus, a pressure-responsive device; means providing anenclosed space in commimication with said pressure-responsive device and having an escape port whose'discharge end is bounded by a flat surface; means including an orifice for supplying pressure fluid to'said space; speed responsive means operated by the prime mover and having a thrust member means providing a guide aiined longitudinally with said port and thrust member; an elongated member having a stem at one end in abutting relation with respect to said thrust member, having a cup in covering relation with respect to the exit end of said port and cooperating with the fiat boundary surface to provide a radiau ..directed annular escape orifice, and having a slide portion fitting the guide; the end of said slide portion remote from the port providing a piston area in opposed relation to that provided by the cup and bounded by the annular orifice and said guide and cooperating with saidflat boun surface space and the providing a chamber for the first piston area and means including a passage connecting said space and chamber and providing for lagging of pressure changes in the chamber relative to said space. a

13. In governing apparatus, SUPI'CSSUIG-TCSDOH- sivedevice; a centrifugal governor including flyweights, spring means, and a thrust member acted on by opposing efiects ,of thefiyweights and of the spring means; and a pressure transl a former providing transformed fluid pressure for acting on the pressure-responsive device; said transformer including means providing an enclosed transformed fluid-pressure space in communication with the pressure-responsive means and provided with an escape port bounded by a flat surface extending normally with respect thereto, means including an oriflceior supplying fluid under pressure to said space, means providing a guide alined longitudinally with said port and the thrust member, and a member in thrust-transmitting relation with respect to said thrust member and provided with a cup having a thin annular edge cooperating with said flat sure face to provide a radially-directed circular escape orifice, said member having a slide portion fitting the guide. I Y

'14. In governing apparatus, fiyweights spring means, a thrust member acted on by theresultant of forces due to the flyweights and the spring means, means providing a space for liquid-under regulated pressure, said lasts-named means comprising a housing provided with a'bore' and a t u bular member slidable in the bore toward "and away from said thrust member and providing a discharge port for said space, a member in thrust transmitting relation with respect to said. thrust member and provided with a portion arranged in covering relation with respect to said discharge port and cooperating with the discharge end of i the tubular member to define an annular escape orifice for said space, means for supplying liquid to said space so that the pressure therein depends upon the' fiow area of the escape orifice, and means for adjusting the tubular member toward and away from said thrust member to provide,

"for a given escape area of the annular orifice and the corresponding regulated pressure, a change in speed dependent upon the extent and direction of adjustment.

15. In governing apparatus, fiyweights, spring means, a thrust member acted on by the resultant of forces due to the flyweights and the spring means, means providing a space for liquid under regulated pressure, said lastrnamed means comescape orifice, means including a metering oririce for supplying liquid to said space, and means for adjusting the tubular member toward and away fromsaid thrust member to provide, for a given escape .area of the annular orifice and the 'correspondingregulated pressure, a change in speed dependent upon the extent and direction of adjustment. I

MANIOUS GO'I'I'LIEB.

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