US2101486A - Prime mover governing system - Google Patents

Description

Dec. 7, 1937. v. I. ZELOV 1 PRIME MOVER GOVERNING SYSTEM I Filed April 3, 1955 2 SheetsSheet 1 IN VEN TOR.

Dec. 7, 1937. v ZEL V 2,101,486

PRIME MOVER GOVERNING SYSTEM Filed April 5, 1935 2 Sheets-Sheet .2

' INVENTOR. WITNESS PIQ. mwsm Patented 7, 1937 UNITED STATES PRHVIE MOVER GOVERNING SYSTEM victor I. Zelov, Rosemont, Pa, assignor, to Cooperative Engineering Co., Philadelphia, Pa., a corporation of Delaware Application April 3, 1935, Serial No. 14.404

. 15 Claims. My invention relates to a speed governor, particularly for a prime mover, and it has for itsobject to provide a speed governor which transforms changes in the centrifugal force of governor flyweights into corresponding oil pressure changes directly, substantially without governor travel, thereby increasing the speed of response to speed changes of the prime mover. It is further the object of my invention to provide a governor with considerably reduced friction in the governor .relay, thereby increasing the sensitivity of the governor to speed changes. It has for another object the ability of the governor to respond to external control impulses, or operating conditions of the prime mover other than speed in addition to speed changes. Another object of my invention is to allow the use of a small governor, transforming small changes of governor forces into proportionalglarge motive 20 fluid pressure variations. Further objects and advantages of my invention will be apparent from the following description of the device.

Satisfactory governing devices have been'designed for governing prime movers at a given speed. Considerable difficulty has been experienced, however, in obtaining a short time lag between the speed change of the prime mover and the motion of governing valve. My invention provides such a short time lag by an im- 30 mediate response of the transformed pressure .and of the operating mechanism to the smallest speed changes. This is accomplished by substantially eliminating motion of actuating transformed fluid in the pressure transformer, the 'pressure responsive element of the operating mechanism, and in the interconnecting piping. Diagrammatic views of my invention are shown in the drawings:

Fig. 1 shows a governor, governor transformer,

40 admission valve and its operating mechanism with the connecting piping. Fig. 2 shows a diagrammatic arrangement of a prime mover equipped with 3 motive fluid admission valves, which are actuated by the governor transformer system.

Fig. 3 shows a sectional elevation of a pressure transformer relay actuated by a flyweight governor.

Fig. 4 shows a sectional, view of.-'the relay structure of Fig. 3 taken alongline IVIV.

' Fig. 5 is a sectional view of the fluid turbine 7 taken along the line VV of Fig. 3.

Fig. 6 shows a modification to Fig. 2 where an external regulating impulse reacts on an indi-' vidual governing valve operating mechanism.

Referring to Fig. 3 in detail, I show a flyweight governor I having a rotating member 2 suitably connecte'd'to the shaft of the prime mover which is being governed; member -2 carries two flyweights 3 on pivots 4. The flyweights are con-- 5 nected by tension spring 5 and have lever arms 6 suitably connected in joint 7. Plate 8, carried by the lever arms, supports plunger 9 of the governor relay. The tension spring 5 balances the centrifugal force of the flyweights and the force 10 of plunger 9 against plate 8.

The governor relay I 0 consists of a pressure I transformer similar to the transformer described in Letters Patent 1,966,841. In the relay I0 I show a transformer-housing ll having an actul5 ating fluid inlet connection l2 and a transformed fluid discharge connection l3,- drain connection ity and one or several external control pressure connections IS. The housing II has a bore or chamber I6 within which is disposed bushing 11 and regulating sleeve I8, having properly located passages and grooves. Regulating sleeve l8 has a threaded extension 19, engaged by a nut element 20. Nut can be rotated by means of speed changer hand'wheel 2|, or by means of remote control motor which turns worm 22 and worm wheel 23. The rotation of worm wheel 23 is transmitted to nut 20 through friction surface 24 loaded by spring 25. Key pin 26, moving in slot 21 of bushing ll, prevents regulating sleeve l8 from rotating with nut 2D. Plunger 9 is disposed within regulating sleeve 58.

The piston valve 9 fits within the cylinder or regulating sleeve l8 and it has a control port or recess 28 arranged between piston valve portions 28:; and 281), the valve portions cooperating with ports and features of the cylinder as hereinafter pointed out.

-The piston valve is guided by the bushings 29 and 30 extending within the cylinder andcooperating with the elongated journal portions 29a; and 25b of the piston valve. To avoid static friction eifects, the piston valve is continuously rotated by friction between the plate 8 and the face 3| at the lower end of the piston valve, or 5 by means of a hydraulic turbine 33;

The bushing I1 has slots or openings provided therein which cooperate with the interior of the housing bore and theexterior of the cylinder to provide the inlet chamber 34 in communication with theinlet connection I2 for liquid, under pressure, the chamber 35 in communication with the transformed pressure connection 13, the drain chamber 36 in communication with the drain connection It and the pressure chamber 91 in communication with the connection I! for supplying liquid thereto and whose pressure is providing an exhaust port. Port or ports 4! arranged intermediately of the pressure and exhaust ports afford communication of the interior of the cylinder with the chamber. 99 and the transformed pressure connection l9.

The piston valve portions 290 and 29b are so spaced that, with the piston valve in neutral position, the valve portions Just lap the inlet and exhaust ports 99 and 99 such that, with very slight axial movement ofthe piston valve in an upward direction, the inlet or pressure port is placed in communication with the transformed pressure port 42, and, with slight movement in the other direction, 'the latter port is placed in communication with the exhaust port.

The piston valve 9 has flrst and second piston areas or abutments 43 and 44, preferably facing in such a direction that fluid pressure forces applied thereto will be in opposition to the force of the governor. The flrst piston area 49 forms a part of the interior surface of the pressure chamber 45- connected by the port 49 to the transformed pressure chamber 95, and the second piston area 44 forms a part of the interior surface of the pressurechamber 41 connected by -the port 410. to the pressure chamber 91 supplied with fluid under pressure which depends uponan operating characteristic of the prime mover apparatus other, than speed. 1

Assuming a change in load, then, dependent upon the direction of load change, the apparatus operates to bring about a change in secondary -or transformed. fluid pressure, the. pressure diminishing with decrease in load and increase in speed and vice versa. With a change in load and. consequent change in speed, the-equilibrium of forces acting on the piston valve of the transformer is immediately disturbed, the spring load increasing with increase in speed and vice versa; however, the resulting change in the force of transformed or secondary pressure acting on the piston area 49 compensates for the change in spring force with the result that the piston valve is restored to equilibrium position. An increase in pressure in the chamber 41 causes an increase of force acting on the second piston area 44 and produces an effect similar to the eflect of increased speed of the prime mover. An increase in speed of the prime mover and an increase in pressure on the piston area 49 tend to move the piston valve 9 downwardly. Although Fig. 3 shows only one external control pressure chamber 41 and one piston face 44, it will be obvious to those skilled in the art that it is possible to provide a multiplicity of such piston areas or abutments defining the same number of pressure chambers connecting to several external control-pressure sources; moreover, these pressure chambers and the several pressure abutments defining these pressure chambersmaybedisposcdinamanner thatthe II and 49 will fallt control impulses on the piston valve 9 are added to or subtracted from the governor force.

. piston valve 9 carries a hydraulic turbine 41 held in place by set screw 49 and rotated by two reaction jets 49. Actuating fluid is supplied .to the reaction jets 49 through passage 59 conits longitudinal axis, rotating preferably in the same direction as the governor spins the piston valve through plate 9. This hydraulic turbine is provided only when it is not desired to rely solely upon the friction between plate 9 and piston valve 9 for spinning the piston valve. Bushing IT has, as shown in Fig. 3, several passages, these passages disposed both axially and circumferentially to register with the corresponding openings in regulating sleeve I9. Fig. 4 shows a cross-sectional view along line IV-IV illustrating how chamber 35 and inlet chamber 94 are separated by division walls 52.

The operation of the above embodiment of my invention is as follows: It is well known that in a flyweight governor, such as shown in Fig. 3, the flyweights tend to move out with increase of speed. The magnitude of this motion for a deflnite change in speed depends on the spring characteristics and on the mass of the flyweights. At any given speed, the flyweights will assume a certain position, such that all forces acting on the flyweights will be in equilibrium. These forces are: (1) centrifugal force of flyweights, (2) tension of the governor spring 5, (3) the force on the piston valve 9 created by the oil pressure in chamber 45 acting on the piston face 49, and transmitted through plate 8, (4) the force on abutment face 44 if an external control pressure is used.

The spring 5 balances the centrifugal forces and the hydraulic forces on plate 8. Should the speed of the prime mover decrease, due to increase in load, the centrifugal force on weights 9 will decrease accordingly. The force on spring 9 will tend to move the weights inward, thereby causing piston valve 9 to move upward and admit actuating fluid from the inlet port 38 to the transformed pressure port 42 and the chamber 35 communicating therewith. The pressure in conduit from outlet connection I3, leading to the admission valve operating mechanism, will increase and open the admission valve, the increase in pressure will also be transmitted to pressure chamber 45,

' thereby increasing the force on piston valve 9 and plate 9. The"pressure in chamber 35'will increase, till the resulting force on piston valve 9 will compensate the loss of centrifugal force and restore the piston valve to its original position, thereby closing. transformed pressure port 29.

Should the speed of the prime mover increase, due to decrease in load, the increased centrifugal forces on weight 3 will tend to extend spring 5, thereby causing piston valve 9.to move downward, thus opening transformed pressure port 29 to exhaust or drain port 99. Transformed pressure fluid-will be discharged from chamber 95;

- the pressure in chamber 99 and conduit from connection l9 will decrease, and the operating mechanism will close the admission valve. The decrease of pressure in chamber 95 will cause a decrease in chamber 45, and thereby decrease the force of piston valve 9 on plate 9. The transformed pressure'inthe communicating chambers the decrease of force -on plate 9 will compensate th increase in centrifugal force on weights Iv and returnthe piston valve" "piston face 43 is proportioned to be equal /2 sq.

piston valve to bring the latter to neutral posi-- inch, the pressure in chamber 33 will change 60 lbs. per sq. inch to compensate the total centrifugalforce change, provided a 1:1 lever ratio is chosen between the weights 3 and plate 8, as represented in Fig. 3. f

In order to govern at various speeds, I provide a speed changing device which operates as follows:

Regulating sleeve l8 can be moved up and down by means of screw nut 26. It will be clear to those versed in the art that piston valve 9 owing to the tendency of the forces acting on the tion where the valve portions 28a and 282) just lap the inlet and exhaust ports 38 and 39 thereby interrupting comn'iunicai' ion of either of these ports with the transformed pressure port 42 will follow the regulating sleeve l8, so that port 28 registers with grooves 31 and 38. The prime mover will adjust itself to a speed of rotation, such that the. flyweights will return piston valve 9 to the neutral position in which the piston valve portions 28a and 28b just lap the-inlet and ex haust ports so as to interrupt communication thereof with the transformed pressure port. More specifically, a downward movement of regulating sleeve cylinder ill will admit actuating fluid from the inlet port 38 to the transformed pressure port 42. The pressure in conduit from outlet i3 .to admission valve operating mechanism will increase and open the admission valve, thereby increasing the speed of the prime mover. The increased centrifugal force will move weights 3 out and allow piston valve 9 to move down until the transformed pressure valve port 28 is brought into neutral position with respect to grooves 38 and 39. The prime mover will be governed again as described above but at a higher speed. Limit stops 53 are provided to limit'the range of speed change.

From the foregoing, it will be seen that any departure from the neutral position shown in Fig.3

is followed by changes tending to restore such valve to neutral position. If there is a change in load, .then there results immediately a dis-v turbance in equilibrium or forces acting on they piston valve with the result that the valve moves slightly, such slight movement being instantly followed by change in transformed or secondary pressure, and the latter change proceeds until the forces acting on the p'lston'valve are again in equilibrium with the piston valve restored to neutral position. Thus, the governor operates with very little movementof its'parts, with a negligibleamount of friction andvitis highly sensitive and involves only a small amount of lag, particularly as there is little motion, results being secured by pressure variationsand applications, in consequence of all ofvwhlch the percentage of regulation is small. If the'cylinder I8 is moved, then, due to the fact that the piston valve 9 is, by such movement, no longer i'n-the neutral position, the governor will l operate to effect such changes that the forces acting on the piston valve are again in. equilibrium. with the piston valve in the new neutral position determined by the setto an admission valve operating mechanism. Referring to Fig. 1 for a more detailed description of the admissionvalveJt comprises motive fluid regulator 54 and an operating mechanism 56. Body 56 of regulator 54 has a motive fluid inlet connection 57 and an outlet connection 58. Disting of the cylinder. Obviously, there. is a posiposed within the valve body is a valve disc 63 which is actuated by the operating mechanism 66. The operating mechanism has a body portion 60, a piston 6|, a pilot valve 62, actuating fluidports 63 and 64 which communicate respectively with the opposite sides of the piston 6|. The body has actuating fluid inlet port 66 and discharge ports 66 and 61. The pilot valve 62 is formed with piston portions 68 and 69 which cover the ports 63 and 64 in the cut-01f position of the pilot valve. The upper end' of the pilot valve abuts against bellows ill, pilot valve 62 is urged by springfi'l upwardly. Bellows I6 is disposed in pressure chamber, 12. This chamber is supplied by the transformed fluid through a conduit connected to outlet i3 from transformer iii. A lever 13 is connected at one of its ends to piston '6l through piston rod 14 and connecting link 15. The other end of lever I3 is pivoted to the wall of pressure chamber 12 through pin I6. Lever 13 is connected to bellows 16 through adjusting screw 71 and follow-up spring 18. The operation of the mechanism is as follows: an increase in transformed fluid pressurein conduit connected to outlet l3 causes bellows 10 to deflect downward, moving pilot valve 62 downwardly. The downward motion of pilot valve 62 places ports 65 and 63 in communication, thereby admitting actuating fluid under pressure to the lower face of piston 6|, to move same in a valve opening direction. At the same time ports 64 and 61 are brought intocommunication permitting fluid from the upper face of piston 6| to-be discharged through conduit 19. As piston 6| moves upward, it moves the left end of lever 13 upwardly about pivot pin 16 and so extends followup spring 18 until the bellows and pilot valve 62 are returned'to the original cut-off position.

A decrease in transformed fluid pressure in conduit to outlet l3 will cause bellows 10 to move up ward being urged by the tension of the-spring 16. Pilot valve 62 will follow the bellows movement due to action of spring II. The upward movement of valve 62 will place ports 65 and 64 in communication, thereby admitting actuating fluid under pressure to the upper face of piston 6|, to move same in valve closing direction. At the same time ports 63' and 66 are brought in' communication, permitting fluid from the lower face of piston 6| to bedischarged through conduit 19. As piston 6| moves downward, it moves the left end of lever 13 downward about'pivotpin 16, thereby releasing the tension on follow-upspring 18 until bellows I6 and pilot valve 62 are returned 7 passage 8| in chamber 80 formed inside the bellows, thus providing means for controlling the admission valves from an external-control pressure in addition to speed control from transformer l0.

Figure 1 shows a sectional elevation of the admission valve operating mechanism, connected to turbine or prime mover 92. The turbine shaft 89 drives through .worm 99 and worm wheel 85 the governor shaft 99, which rotates governor I and actuating fluid pump 91, in a conventional manner. The pump discharge 99 supplies the actuating fluid to pressure transformer I9 and operating mechanism 99 through conduits and 99, respectively. The discharge from the operating mechanism 99 drains to the pump suction 9| through conduit 92. The actuating fluid is supplied at a pressure preferably 15 lbs. per'sq.,inch higher than the maximum transformed pressure to the operating mechanism.

If a prime mover is used as a base load machine, it may be desirable to retard the response of the admission valve operatingmechanism to speed fluctuations, thereby making the machine insensitive to quick transient disturbances of the system. The retardation of response permits a relatively quick disturbance to end before the admission valve operating mechanism would have time to move the motive fluid inlet valve- In the same time ordinary changes in the speed of the machine will be responded to. To accomplish this retardation of response, I providea needle valve 99 in the conduit in the transformed pressure outlet I9, as shown in Fig. 1, and an air bell 99 disposed between the needle valve 99 and operating mechanism 59. This' retarder of response functions as follows: Any change in speed of the unit will produce a substantially immediate change in the transformed pressure of the fluid in the section of the conduit between outlet I9 Opening I9I admits motive fluid to all three governor valves, which control the admission of motive fluid to three nozzle chambers of the turbine in a conventional manner. The re'spec' tive governor valve operating mechanisms 99, 99, .and I99 are shown to a large scale in Fig. 1. Figure 2 shows further'the shaft driven governor I, the pressure transformer l9; i't also-shows operating fluid pump 91 supplying actuating fluid under pressure through conduit 99 to the transformer I9 and the three valve operating mechanisms 99, 99 and I99. The conduit'frorn outlet I9 in transformer I9 supplies transformed pressure fluid to the three valve operating mechanisms 99, 99, and I99 respectively. .The return conduit 92 drains the discharge from the valve operating mechanisms to the suction 9I of' pump 91.

The operation of each individual operating mechanism 99, 99, and I99 is the same as the operation of the operating mechanism 99 shown in Fig. l and described above. It iscommonly desirable to operate the governing valves 95, 99,

and- 91 as primary, secondary and tertiary ad- They are then operating in se- This may be mission valves. quence and in overlapping relation.

very easily accomplished by installing proper springs 19 in the respective operating mechaating mechanism 99.

amuse nisms. These springs having such relatively different initial loads and scales, that the opening of each successive valve precedes the closing of the prior valve, thus obtaining uninterrupted and continuous flow of motive fluid to the prime function of the operation of the prime mover.

The auxiliary transformer consists of pressure responsive element I99 and the transformer proper I99. This transforms the primary pressure changes, in element I99, into external control pressure variations, in the proper ratio to produce a predetermined travel of the admission valve 99, 99', or 91 on the prime mover, for any variation of the controlling pressure in I99. Conduit I99 supplies the actuating fluid to the auxiliary pressure transformer I99, while the transformed external control pressure can be connected either directly to the governing transformer I9 through conduit I99, or to'an individual governor valve operating mechanism, say, 99 through conduit ,I9'l as shown in Fig. 6. In the flrst casethe variation of pressure in I99 affects all admission valve operating mechanisms in their proper relation, as established by their' adjustment; in the second case, a variation in pressure in I99 afiects only admission valve oper- It is understood that either or all of the operating mechanisms can be connected to the auxiliary transformer I94.

My governing system described in the above has an increased degree of sensitivity because the time lag between a change in speed of the prime mover and the responsive movement of the pilot valve of the governing valve operating mechthe flow of actuating fluid to the valve operating piston is in my governor the same as in the other conventional governors, and is determined by the size and stroke of the operating piston, size of the pilot valve, andthe capacity of the actuating fluid pump. Howeverfin conventional governing systems where mechanical linkage is used between the governor and the pilot valve of the governing valve operating mechanism, the time lag between a speed change of the prime mover and the responsive movement of the pilot anism is practically eliminated. The additional .time lagin the operating mechanism caused by valve is determined by the inertia and friction in the connecting linkage. In larger units, where this inertia and friction become too large. for the governor to overcome, an auxiliary hydraulic voperating mechanism is,introduced, in order to keep the time lag within limits of stable governing; in this case, the time 'lag between the speed change of the prime mover and the responsive movement of the pilot valve of the governing valve operating mechanism is the combined time lag caused by the inertia and friction in the connecting linkage from the governor to the relay of the auxiliary mechanism, and the time necessary to fill the operating cylinder of this mechanism by actuating fluid under pressure. A similar time lag is existent in any governing system in which motion is employed to obtain a movement of the pilot valve of the governing valve operating mechanism, responsive to a speed change of the prime mover. In my governing system, the

several elements converting a speed change of the prime mover 82 into a response of the pilot valve 62 of the governing valve operating mechanism 55 remain practically in their neutral position throughout the total governing range, the

governor relay plunger 9 deviating from its original cut-off position only momentarily through a very small distance, suflicient to establish a fluid pressure change in chamber 33 to balance out the change of centrifugal force on weights 3, caused by the change in speed of the prime mover. The pilot valve 62 and the bellows l remain also practically in the cut-oil position of the pilot valve throughout the governing range of the prime mover, deviating from this position only through an inappreciable distance suflicient to admit actuating fluid to the operating piston 6!, which by its movement returns pilot valve 62 to its cut-ofl' position. Experience has shown that the actual deviations from the cut-off position of both plunger 9 and pilot valve 62 do not exceed five thousandths of an inch even in the larger prime movers. It is therefore evident that no substantial flow of fluid, or motion of mechanical parts is required to convert a change in speed of the prime mover 82 into a response of the pilot valve 62 of the governing valve operating mechanism, thus reducing considerably the time lag between this response and the speed change of the prime mover, and increasing correspondingly the sensitivity of my governor system.

From the above description, it will be seen that I have provided a governing mechanism which is readily adaptable to various applications, where flexible and sensitive governing is desired. While I have shown my invention in but one form, it will be obvious to those skilled in art that it is not so limited, but is susceptible of various changes and modifications without departing from the spirit thereof, and I desire therefore that only such limitations shall be placed thereon as are imposed by the prior art or as are specifically set forth in the appended claims.

I claim: I

1. In a governing system for a prime mover having an admission valve and means for operating the admission valve and including a pressureresponsive control device, a combination of means w for developing centrifugal forces varying as a function of the speed of the prime mover, a plunger construction having an abutment for receiving said centrifugal forces and having a plurality of pressure faces, a housing around the plunger construction defining pressure chambers with said pressure faces, means responsive to an operating condition other than the speed of the prime mover and providing an external control fluid pressure varying as a function of said operating condition, means to' conduct-said external control fluid pressure to one of said pressure chambers, means including said plunger and responsive to centrifugal force and. said external control fluid pressure to provide a secondary fluid pressure, means for supplying fluiti under secondarypressure to the second of said pressure chambers to balance the centrifugal and the external control fluid pressure, andmeans for sup- .plying fluid under secondary pressure to said pressure-responsive device. I

2. In a governing system for a prime mover, the combination of a flyweight governor, means for transforming centrifugal force of the governor into fluid pressure, admission valves for said prime mover, motor devices for operating the same comprising a fluid pressure relay for each valve, a housing for each relay, pressure responsive means in each housing controlling the relay therein, said pressure responsive means being subjected to said fluid pressure and external control pressure responding and varying as a function of an operating condition of a prime mover other than its speed, restoring means moved by the operating piston of the motor device toreturn the pressure responsive means to neutral position, said restoring means restricting the travel of the operating piston to be in proportion to changes in said fluid pressure or changes in said external control pressuraor to the sum of or the difference between the changes of both pressures. a

3. The combination with a prime mover having an admission valve, of a pressure-regulating device providing fluid under regulated pressure and including a control element which is operative to vary the magnitude of regulated pressure, a centrifugal governor operated by the prime mover and arranged to impress its force on the control element, means for applying to the control element a force opposed to the governor force and which is a function of the regulated pressure, whereby there is provided a predetermined range of regulated fluid pressures for the range of govfor exerting force in opposition to that of regulated' pressure to restore the control valve to neutral position.

4. The ,combination with a prime mover having an admissionvalve, of a pressure-regulating device providing fluid under regulated pressure and including a control element which is operative to vary the magnitude of regulated pressure, a centrifugal governor operated by the prime mover and arranged to impress its force on said control element, means for applying to the control element a force-opposed to the governor force and which is a function of the regulated pressure,

an admission valve operating element, a con-" trol valve movable slightly in opposite directions from a neutral position for controlling the application of motive medium to the operating element to secure more orrless restricted opening of the admission valve, means for moving said control valvefrom neutral position and including an abutment subjectto regulated pressure and opposing spring means, and means responsive to movement of the admission valve, operating element for changing the force of the spring meansto restorethe control valve to neutral position.

5. The combination with a prime mover having an admission valve; of a pressure-regulating device providing fluid under regulated pressure;

said device including a control element normally occupying a neutral position and movable a slight amount, in one direction, to increase the regulated pressure, and, in the other direction, to reduce the regulated pressure; flywelght means operated by the prime mover for developing a centrifugal first force;- spring means providing a second force; means providing a third force'which is a function of the regulated pressure; means providing for application of said forces to the control element with the second force opposing the flrst and third forces; an admission valve operating element; a control valvemovable slightly in opposite directions from a neutral position for controlling the application of motive medium to the operating element; means for moving said control valve from neutral position and including an abutment subject to regulated pressure and opposing spring means; and means responsive to movement of the admission valve operating element for changing the force of the spring means to restore the control valve to neutral position.

6. The combination with prime mover apparatus having an admission valve and means responsive to magnitude of the fluid pressure with negligible fluid flow for controlling the valve, of a pressure-regulating device connected to the pres sure-responsive means for maintaining fluid for the latter under regulated pressure; said device including a controlling element normally occupying a neutral position and movable a slight amount, in one direction, to increase the regulated pressure, and, in the other direction, to reduce the regulated pressure; centrifugal means operated by the prime mover for developing a first force; spring means providing a second force; meansproviding a third force which is a function of the regulated pressure; means providing a fourth force dependent upon an operating characteristic of the apparatus other than speed; and means providing for application of said forces to the control element with the second force opposing the first, third, and fourth forces.

7. The combination with a prime mover having an admission valve, of a pressure regulating device providing fluid under'regulated pressure; said device including a piston valve normally occupying a neutral position and movable axially a slight amount, in'one direction, to increase the regulated pressure, and, in the other direction, to reduce the regulated pressure; centrifugal means operated by the prime mover for develop ing a flrst force; spring means providing a sec-' ond force; means providing a third forcewhich is afunction of the regulated pressure; means providing for application of said forces to the piston valve with the second force opposing the first and third forces and in such relation that, when the control element movesin, response to change in centrifugal force, it moves in such a direction as to change the regulated pressure inversely until the resulting changing third force attains a value such that the forces are restored to equilibrium with the control element in neutral position; an admission valve operating element; a control valve movable slightly in opposite directions from a neutral position for controlling the application of motive medium to the operating element; means for moving said control valve from neutral position and including an abutment sub- Ject to regulated pressure and opposing spring means; means responsive to movement of the admission valve operating element for changing the force of the spring means to restore the control valve toneutral position; and means providing for adjustment of the regulating device so as to vary the element. V 8.- The combination with a prime'mover having an admission valve, of a motor device for actuating the valve; a pilot valve controlling neutral position of the control operation of the motor device; means providing opposing first and second forces for normally maintaining the pilot valve in neutral position; said last-named means including a centrifugal governor, means for transforming centrifugal force of the governor into fluid pressure, means utilizing said fluid pressure to provide the first force acting on the pilot valve; and means responsive to operation of the motor device for modifying said second forceto restore the pilot valve to neutral position.

9. The combination with a prime mover having an admission valve, of a governor operated by the prime mover and including flyweight means for developing centrifugal force and biasing means acting in opposition to the centrif ugal force in order to provide a resultant force; a pressure transformer including a cylinder and a piston valve; said cylinder having inlet and exhaust ports and a transformed pressure port; said piston valve having valve means thereon arranged normally to cover the inlet and exhaust ports such that slight movement of the piston valve, in one direction, places the transformed pressure port in communication with the inlet port and, in the other direction, places the transformed pressure port in communication with the exhaust port; means providing for the application of said resultant force to said piston valve; means for supplying liquid under pressure to the inlet port; means providing for the application of liquid under transformed pressure to the piston valve such that the force thereof is exopposite directions from a neutral position for controlling the application of motive medium to the operating element to secure more or less restricted opening of the admission valve; means for moving said control valve from neutral position and including an abutment surface subject to fluid under transformed pressure and opposing spring means; and means'responsive to movement of the admission valve operating element, for changing the force of the spring means to restore the valve to neutral position.

10. The combination with prime mover apparatus having an admission valve and a pressure responsive device for controlling the valve position, of a governor operated by the prime mover and including means for developing centrifugal force and biasing meansacting thereon in opposition to the centrifugal force in order to develop a'flrst controlling force; a pressure transformer including a cylinder and a piston; said cylinder having inlet and exhaust ports and a transformed pressure port; said piston having valve mans thereon arranged normally to cover the inlet and exhaust ports such that slight movement of the piston, in one direction, places-the transformed pressure port in communication with the inlet port and, in the other direction, places the transformed pressure port in communication with the exhaust port; means for supplying liquid under pressure to the inlet port; means for supplying liquid under transformed pressure from the trans--. formed pressure port to said pressure responsive device; means for developing a second controlling force responsive to an operating characteristic of the apparatus other than speed; means providing for the application of the first and second controlling forces to the piston valve axially of .the latter and in opposed relation; and means providing for the application to the piston valve of a force in the same direction as the second force and dependent upon the magnitude of transformed pressure.

11. The combination with prime mover apparatus having an admission valve and a pressure responsive device for controlling the valve position, of a governor operated by the prime mover and including means for developing centrifugal force and biasing means acting thereon in opposition to the centrifugal force in order to develop a first controlling force; a pressure transformer including a cylinder and a piston valve; said cylinder having inlet and exhaust ports and a transformed pressure port; said piston valve having valve means thereon arranged normally to cover the inlet and exhaust ports such that slight movement of the piston valve, in one direction, places the transformed pressure port in communication with the inlet port and, in the other direction, places the transformed pressure port in communication with the exhaust port; means for supplying liquid under pressure to the inlet port; means for supplying liquid under transformed pressure from the transformed pressure port to said pressure responsive device; means for developing a second controlling force responsive to an operating characteristic of the apparatus other than speed; means providing for the application of the first and second controlling forces to the piston valve axially of the latter and in opposed relation; means providing for the application of a force dependent upon the magnitude of transformed pressure to the piston valve in the same axial direction as the second controlling force; and means providing for axial adjustment of said cylinder relatively to the piston valve, whereby the transformed pressure may be varied relatively to the first and second controlling forces to effect speed changing adjustments of the apparatus.

12. The combination with prime mover apparatus having an admission valve and means responsive to magnitude of fluid pressure with negligible fluid flow for controlling the valve, of a pressure-regulating device connected to the pressure-responsive means for maintaining fluid for the latter under regulated pressure; said device including a controlling piston valve normally occupying a neutral position and movable axially to a slight extent, in one direction, to increase, and, in the other direction, to'decrease the regulated pressure; a governor including flyweights, spring means opposing the centrifugal effect of the flyweights, and an actuated abutment connected tothe flyweight; said abutment being arranged in abutting relation with respect to one end of the piston valve; said piston valve having first and second piston areas facing away from the governor; means for applying fluid under regulated pressure to the first piston area; means providing fluid whose pressure is dependent upon an operating characteristic of the apparatus other than speed; and means for applying; the last-named pressure to the second piston area.

13. The combination with prime mover apparatus having an admission valve, of a governor operated by the prime mover and including means responsive to centrifugal force and biasing means acting thereon in opposition to centrifugal force in order to develop a first controlling force; a fluid controlled system including a cylinder, a piston valve for the cylinder, and a pressure responsive device for controlling the admission valve; said cylinder having inlet and exhaust ports and a transformed pressure port; said piston valve having valve means thereon arranged normally to cover the inlet and exhaust ports such that slight movement of the piston valve, in one direction, places the transformed pressure port in communication with the inlet port and,

in the other direction, places the transformed pressure port in communication with the exhaust port; means providing for the application of said first controlling force to said piston; means for supplying fluid under pressure to the inlet port; means for supplying fluid under transformed pressure to said pressure responsive device; means for developing a second controlling force responsive'to an operating characteristic of the apparatus other than speed; and means for supplying the second controlling force to said system such that the pressure-responsive device moves the admission valve responsively to both controlling forces.

14. In a governing system for prime mover apparatus having an admission valve, a governor of the fly-weight type operated by the apparatus, means utilizing the governor to provide a first fluid pressure, means providing a second fluid pressure varying as a function of an operating condition of the apparatus other than its speed, an admission valve operating element, a control valve movable slightly in opposite directionsfrom a neutral position to control the application of motive medium to the operating element to secure more or less restricted opening of the admission valve, means responsive to changes in said first and second fluid pressures for moving the control valve from neutral position, and means responsive to movement of the admission valve operating element for restoring the control valve to neutral position. v

15. In a governing system for prime mover apparatus having an admission valve, a governor of the fly-weight type and operated by the apparatus. means utilizing the governor to provide a first fluid pressure, means providing a second fluid pressure varying as a function of an operating condition of the apparatus other than speed, an admission valve operating element, a control valve movable slightly in opposite directions from a neutral position to control the application of motive medium to the operating element to secure more or less restricted opening of the admission valve, means for controlling the position of the control valve including abutment areas subject to said first and second pressures and spring means, and means responsive to movement of the admissi n valve operating element for changing the force of the spring means to restore the control valve to neutral position.

. VICTOR I. ZELOV.

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