US1544238A - Governor - Google Patents

Description

June 30, 1925. 1,544,238

r A. "r. KASLEY GOVERNOR Filaaan. 5. 1925 a Sheets SH e'et 1 ATTORNEY June 30, 1925. 1,544,238

A. T. KASLEY Y GOVERNOR Filed Jan. 5, 1925 3 Sheets-Shee't 2 1% A'TJWIW ()VV VI ESSESZ I ww- ATTORNEY June 30, 1925.

A. T. KASLEY GOVERNOR Filed Jan. 5. 1925 3 sheets sheet 5 WyN ESSE? ATTORN EY Patented June 30, 192 5.

UNITED STATES ALEXANDER T. KASLEY, OF ESSINGTON,

HOUSE ELECTRIC AND MANUFACTURING COMPANY,

SYLVANIA- PATENT 0mm.-

PENNSYLVANIA, ASSIGNOR' TO WESTING- A CORPORATION OF PENN- GOVERNOR.

Application filed January 3, 1923. Serial No. 610,514.

To all whom it may] concern:

Be known that I, ALEXANDER T. KASLEY, a citizen of the United States, and a resident of Essington, in the county of Delaware and State of Pennsylvania, have invented a new and useful Improvement in Governors, of which the following is a specification.

My invention relates to governing mechanism, more particularly of the fluid pressure type, and it has for its object to provide apparatus of the characterdesignated which shall be economical to build and to operate,

which shall be reliable and stable in operation, and which shall be capable of maintaining closely regulated speeds for different loads imposed upon a machine with which the governing mechanism is associated.

Another object of my invention is to provide fluid-pressure actuated governor mechanism which shall be capable of interrupting the supply of energy to a machine should the supply of pressure fluid to the governing mechanism fail or should parts of the governing apparatus break.

A further objectof my invention is to provide a fluid-pressure governing mechanism whose exhaust is utilized for the purpose of lubricating any suitable parts or bearlngs.

Apparatus made in accordance with my invention is illustrated in the accompanying drawings, forming apart of this application, in which Fig. 1 is a side elevation of a turbine showing my improved'governing apparatus applied thereto; Fig. 2 is a diagrammatic and sectional view of the governing apparatus shown in Fig. 1; Fig. 3 is a sectional detail view on a larger scale of a constant:pressure valve shown in Figs. 1 and 2; Fig. 4 is a detail view showing how the housing for the speed-responsive mechanism is supported; and Fig. 5 is a diagrammatic view of distant-control mechanism.

Referring now to the accompanying drawings' for an understanding of my invention, I show a motor or prime mover, at 10, for example, a steam turbine, having an energycontrolling device or admission valve, at 11,

A the valve being moved in opening and closing directions in accordance with the load by means of fluid-pressure governing'mechanism which is operated by the shaft 12 of the prime mover.

The fluid-pressure governing mechanism comprises a pump '13 which delivers fluid under .presure to a. motor device, at 14, the latter being connected to the energy-controlling device or admission valve, at 11, and a speed-responsive, pressure-relieving mechanism, at 15, being provided in order to secure operation of the apparatus in a manner to be described. 7

The pump 13 may be of any suitable type. and it is driven bymeans of a shaft 16 which is geared to the prime-mover shaft 12 by means of any'suitable gearing, at'17.

See Fig. 4. The pump receives flu1d from the storage reservoir 18 and delivers it under pressure through the passageway 19 to the motor device, at 14. In order that the pressure of fluid delivered to the motor device, at 14, may be constant, a ressure-regulating valve 20 is associated wit a passageway 21, communicating with the passageway 19, as may be seen from Fig. 3, the pressure-regulating valve 20 serving to limit the maximum attainable pressure of fluid in the passageway 19. Therefore, the pump ,is

capable of delivering fluid at a substantially the spring or biasing means'29 serves to impart closing movement to the valve 11 so that, should the pressure of fluid fail, closure of the valve 11 is assured. The motor device includes suitable valve ineehani'sm-for controlling the admission and exhaust of fluid to the cylinder or chamber 23, whereby actuated.

The valve mechanism for the operating cylinder'comprises a valve chamber 30, arranged in the head 31 for the operating cylinder 23. The head 31'is provided with a chamber or passage 32, which communicates with the pressure-supply passageway 19 and with the valve chamber 30. An exhaust passage or chamber 33 is provided in the head aggerated manner in Fig. 2 for purposes of 31- and it communicates with the valve chamber 30. A supply passage 34 communicates with the operating cylinder 23 and it is provided witha portion 35 which communicates with the valve chamber, the latter portion communicating with. the valve chamber 30 between the connections of the pressure-supply and exhaust chamber or passages 32 and 33 therewith.

A valve 36, preferably of the piston type,

fits in the valve chamber 30 and it is provided with a piston valve portion 37 whose length is substantially equal to that of the passage 35. The piston valve is provided with reduced portions 38 and 39, above and below the piston portion 37. As the piston portion 37 has 'anedge fit with the sides of the passage 35, when the valve is in its neutral position, it will be apparent that movement of the valve upwardly from this position laces the pressure-supply passage or cham er 32 in communication with the operating cylinder 23 and that downward movement of the valve places the exhaust chamber or passage 33 in communication withthe operating cylinder. The piston valve 36 is preferably arranged coaxial with respect to the rod 25and it has a close clearance 41 with respect thereto for a purpose to be described.

When the piston valve 36 moves upwardly in response to an increase in load on the prime mover, the pressure-supply passage or chamber 32 is placed in communication with the operating cylinder 23, whereupon the operating piston 24 is moved downwardly to open the valve 11 wider to admit an increased quantity of motive fluid to the prime mover in order to take care of the increased load. This downward movement of the operating piston 24 is accomplished by a compression of the spring 29, whose eflect will be more fully hereinafter set forth. \Vith a decrease of load on the prime. mover the piston valve 36 moves downwardly to place-the operating cylinder in communication with the exhaust by way of the passages 34 and 35, the reduced portion 38, and the exhaust chamber or passage The operating mechanism for the piston valve 36-to secure the upward and downward -movements thereof referred to comprises a piston, element, or abutment 42 connected to the piston valve 36 and arranged within a cylinder or chamber 43. The piston has a stem 44 on the opposite side from the piston valve and the piston and stem structure have a close sliding fit with respect to the rod 25. As .shown, the stem 44 extends through the head 45 of the cylinder 43 and it abuts the lower end of the spring 29, the latter being normally held under compression between the stem and an abutment 46, such as a nut, on the rod 25.

The clearance space 41 (shown in an exclearness) between the rod 25 and the interior of the piston valve 30 constitutes an orifice connection for the space of the cylinder '43 beneath the piston 42, this orifice connection including ports 47, whch afford and itwill be seen that its force opposes the fluid pressure forces applied to the operating piston 24 and to the piston 42.

The piston 42 is moved downwardly due to the force of the spring 29 and it is moved upwardly due to flu'id pressure effective beneath the piston 42 whenever the effective force of such pressure exceeds that of the spring. When the piston 42 occupies such a position that the piston portion 37 of .the piston valve 36 is in a neutral position, then the piston 42 is in an'equilibrium position, that is, the force of the spring 29 acting above is counteracted by an opposed and equal effective fluid pressure force applied beneath the piston 43 and beneath the piston portion 49 of-the piston valve. In order thatthe fluid pressure beneath the piston 42 may be maintained substantially conprises a passageway 50 which is connected to the speed-responsive, pressure-relieving mechanism. at 15. The speed-responsive, pressure-relieving mechanism tends to restrict the discharge of fluid whenever the speed of the turbine drops slightly due to an increase in load, with the'resultthat pressure beneath the piston 42 builds up to move the piston valve 36 upwardly in order that fluid under pressure may pass from the chamber or passage 32 by Way of the reduced portion 39 and the passages 35 and 34 to the operating cylinder 23 for the purose of moving the piston 24 downwardly in order to open wider the-energy-controlling device or admission alve 11 to admit an increased quantity of'motive fluid to the prime mover. This downward movement of of the operating the piston 24 continues until the tension ofthe spring 29 is substantially equal to the effective fluid-pressure force acting beneath the piston 42 and the piston face 49 at which JllIlO the piston valve ,36 occupies a ncutra or cut-off position.

With an increase in speed of the prime mover, incident to a decrease in load, pressure beneath the piston 42 is relieved, with the result that the piston is forced downwardly by the spring 29, thereby connecting the operating cylinder 23 with the exhaust chamber or passage 33 by way of the passages 34 and 35 and the reduced portion 38 of the piston valve, whereupon the spring 29 is then effective to move the operating piston 24 upwardly. This upward movement of the operating piston '24 and its rod 25 results in movement of the valve 11 in a closing direction. The upward movement piston 24 is accompanied by a diminution in the force or compression of the spring 29; and, when the compression of the spring 29 is reduced so that the force thereof is substantially equal to the force of the fluid pressure effective beneath the piston 42, then the latter moves to equilibrium position with the piston valve 36 in a neutral or cut-off position.

It will, therefore, be seen that any change in load upon the prime mover is accompanied by a disturbance of the condition of equilibriun'i of the forces acting on the piston valve structure, with the result that the operating piston 24 is moved to secure movement of the admissionva-lve 11 in the proper direction, this movement of the operating piston continuing until equilibrium of forces acting thereon is restored at which time the piston valve 36 occupies a neutral or cut-off position.

The speed responsive relief or bleeder apparatus comprises a hollow shaft 51, which is secured to the upper end of the pump shaft 16, and which communicates with the passageway by means of ports 52, communicating with an annular cham ber 53, the latter being connected to the passageway 50. The hollow shaft carries a suitable head 54 at its upper end, this head being provided with a bottom 55 and a part-ition 56-spaced above the bottom, the partition defining, with the bottom, an exhaust receiving chamber 57. The partition 56 and. the bottom 55 are provided with openings to receive the valve cylinder 58- which is axially alined with the hollow passage 59 of the shaft 51. The cylinder 58 is provided with ports 60 which are covered and uncovered in operation by means of a piston 61.

move thepiston 61 upwardly to open the ports 60. A spring 66 is connected to the arm 64 and to-the head 54 and its force opposes the centrifugal effect of the weight 65 and it tends to move the piston 61 downavardly to close the ports 60. In addition to the opposing forces just mentioned, acting on the piston valve 61, the force of the fluid beneath the piston 61 is also effective in determining the position thereof. In operation, whenever the piston 61 occupies a given position, the force of the fluid effective beneath the piston 61 added to the centrifugal force effective on the weight 65 equals the force of the spring 66.

Theconnection of the spring 66 with the arm 64 is of the adjustable type so-that the tension of the spring 66 maybe varied for the. purpose of'changing the normal speed of the prime mover. As shown, this adjustable connection consists of a threaded anchor member- 67 -for'one end of the spring 66 which has threaded engagement with a screw 68 carried by the arm 64. Thetension of the spring 66 may be varied merely by turning the screw 68 in one direction or the other.

Thoexhaust chamber 57 communicates with a collection chamber 69 by means of ports 70. The collection chamber is formed by a part of the stationary structure which includes the chamber 53; and, beyond the collection chamber 69, such stationary structure extends outwardly as indicated at 71 to constitute the bottom of the housing 72 for the rotary head 54. A drain 71' is shown in the bottom structure 71. The exhaust passage orch'amber 33 in the head 31 is con nected to an exhaustpassageway 73 which leads to bearingsindicated at 74 requiring lubrication. If desired, the space beneath the piston 24 may be connected to the passageway 73 by means of a suitable passageway 75. Also, if desired, the passageway leading from the constant pressure valve 29 pressure passage or chamber 32 of the-opcrating cylinder head 31, such pressure be ing maintained substantially constant due to the employment of a constant pressure valve 20. Fluid under pressure fiows from the pressure chamber or passage 32 to the space inthe cylinder 43 beneath the piston 42 by way of the orifice connection constitutedby the hole 47 clearance space 41 between the piston valve 36 and the rod 25.

The spring 29 under initial compression movement in a closing direction to the valve A For normal operation of the prime mover at a given load, the piston valve 36 occupies a neutral or cut-off positiom'the piston 42 being maintained in an equilibrium posi tion, .the force of the spring 29 thereon being balanced by the fluid pressure force effective beneath the piston 42 and beneath the face 49.

Since fluid is being supplied to the space beneath the piston through the orifice connection, it is necessary, for agiven speed, that fluid shall be -bled from the cylinder 43 beneath the piston 42. Therefore, for all speeds, there is more or less bleeding of fluid through the passageway 50, the passageway 59, and the ports 60, the restriction of the latter being under the control of the piston valve 61.

For a given speed and load, the piston 42 is maintained in equilibrium position by an oil pressure acting therebelow, which, in turn, is maintained substantially constant by the valve 61 cooperating with the ports 60, that is, the valve 61 occupies a given position which depends upon the force of the oil pressure acting beneath the piston 61, upon the centrifugal force effective on the (pgeight 65 and upon the tension of the spring If the'load on the prime mover should increase, the speed thereof would drop slightly with the result that the centrifugal force of the weight member 65 would decrease, thereby disturbing the equilibrium condition-of the forces acting on the piston 61 and permitting the spring to move the piston 61 ggwnward to restrict the passages or ports Therestriction of bleeding from the cylinder 43 results in thebuilding up of pressure beneath the piston 42 and, the fluid pressure exceeding the force of the spring 29, the piston 42 moves upwardly to establish communication between the pressure supply chamber or passage 32 and the oper-. atmg cylinder 23 so that fluid under pressuremay act on the piston 24 to move the admission valve in an opening direction to supply an increased quantity of motive fluigl to the prime mover to meet the increased load.

Whenever there is a decrease in load, resultlng in a decrease in fluid pressure beneath the piston 42, the piston valve moves downwardly to connect the operating cylinderwith the exhaust, whereupon the spring 29 is effective to pull the piston 24 upwardly to move the admission valve 11 in a closing direction to restrict the flow of motive fluid to the prime mover. This upward movement of the operating piston continues until the force of the spring 29 is diminished sufficiently so thatthe piston 42 can return to neutral position.

If the pressure of fluid for the governing mechanism should fail, the pressure of the spring 29 would immediately exceed the pressure of fluid beneath the "piston 42, whereupon the latter would move downwardly to place the operating cylinder 23 in communication with the exhaust chamber or passage with the result that the operating piston 24 and the rod 25 would move upwardly and the admission valve 11 would move in a closing direction due to the forceof the spring 29. If the spring 66 of the speed-responsive device should fail, then the piston valve 61 would be free to move to expose to a greater extent the ports under the influence of the weight and the pres sure of fluid effective beneath the piston. valve 61. The sudden reduction of fluid pressure beneath the piston 42 in this way results in the downward movement of the latter and the movement of the admission valve in a closing direction under the in- I fluence of the spring 29 in the manner just staged.

In operation there is more orless leakage beneath the piston 42 in order that the latter may acquire an equilibrium position. The greater the back pressure the less the Speed. of theiprime mover for the reason that it is necessary that the piston valve 61 restrict the bleeding of fluid from beneath the piston 43 to an extent suflicient to obtain an equilibrium condition of this piston. Accordingly, therefore, I show a pressure regulating valve associated with the head 45 for regulating the back pressure in the cylinder 43 and'above the piston 42.

The. pressure-regulating valve comprises a valve member 76 which cooperates witha seat provided at one end of the outlet passage 77. A spring 78 abuts against oneend ofthe valve member and the other end of the spring abuts against an adjustable member 79, which may be adjusted for the purpose of varying the compression of the spring 78, whereby the pressure of fluid necessary to raise the valve member 76 may 1,544,288 valve member preferably enters a. chamber The operation of speed changing just re- 80 which communicates with a suitable ferred to is particularly advantageous when drain 81. synchronizing one machine with another.

If the compression of the spring 78 is This operation may be conveniently carried lessened, the speed of the prime mover tends out from a distance, as will be apparent to increase for the reason that the back presfrom Fig. 5. In this view, I show a lever sure above the piston 42 is, less and conse- 82 arranged between the screw 79.,and the quently the fluid pressurebeneath the piston spring 78, the lever being fulcrumed at 83 I 42 to hold the latter in neutral or equilibriand having its other end pivotally connected move upwardly so as to supply fluid under when the back pressure is decreased, the pispressure spring may be readily um position is less, the diminished pressure at 84 with a rod or link 85, which'is conbeneath the piston 42 being obtained by a nected to the diaphragm of a pressure desliightly greater opening of the ports 60 vice'86. One side of the diaphragm, is subwhich takes place due to upward movement ject to atmospheric pressure while the other of the piston valve 61 incident to an increase side is subject to a sub-atmospheric presin speed of the turbine. sure, which may be varied, whereby the The first effect of decreasing the back compresion of the spring 78 may be varied pressure on the piston 42 is for the latter to at will.

The sub-atmospheric side of the regulatpressure to the operating piston 24 to move ing device 86 is connected by means of a the latter downwardly and to open wider passageway 87 with the throat of an ejector the admission valve 11, whereby more mo- 01' aspirator 88, the latter preferably utiliztive fluid is admitted to the'prime mover to ing water at constant pressure which is dissecure the increase in speed already'referred charged axially of the ejector or aspirator to for the purpose of bleeding the pressure by means of a suitable passageway.89. If beneath the piston 42 in order that the latwater is used as the motive fluid of the ter may attain a position of equilibrium. ejector or aspirator, this water may be con- An increase in compression of the spring veniently supplied from the turbine gland 78, results in a diminution in the speed of, supply. In order that the pressure device the prime mover for the reason that as soon 86 may have the subatmospheric pressure as the back pressure is increased in this way, varied, I provide means for bleeding air the piston 43 moves downwardly to place from the atmosphere into the passageway 87. the operating cylinder 23 in communication The air bleeding arrangement preferably with the exhaust, whereupon the spring 29 comprises valve mechanism at 90'which may is effective to move the operating piston 24 he supported by a switch board 91 of a and rod 25 upwardly to move the admission power plant. The valve mechanism controls valve 11 in a closing direction, this movethe admission of air from the atmosphere ment continuing until the fluid pressure efthrough the passageway 92 to the passagefective beneath the piston 42 is equal to the way 87, This valve mechanism preferably opposed back pressure and the pressure 04 comprises a suction operated valve member the spring 29. As soon as the flow Of 11 0- 93 which is biased toward its seat by means tive fluid to the prime mover is restricted, of a spring 94 connected to the valve and its speed drops, with the result that the to a tension adjusting member 95. As centrifugal force of the welght member 65 shown, the tension adjusting member 95 is a declines and the spring member 66contractsimpl l ver fulcrumed at 96 and having a until the speed-responsive device attains a l in djust ent 97 with respect to a, condition of equilibrium. This operation of s ctor 98. -As the tension of the spring 94 the speed-responsive device results in the is increased bleeding of the passageway 87 restriction of bleeding from b ne h the is diminished with the result that the subpiston 42, whereby the fluid pressure, heatmospheric pressure is increased and the neath this'piston' builds up. tension of the spring 78 is'diminished. If

It Will, therefore, be Seen that a equi the tension of the spring 94 is diminished,

rium or neutral p siti n 0f he pist n 2 the sub-atmospheric pressure in thepassageis attained, when the bagk P1?Ssure is way 87 is increased with the result that the creased, bOiLh by a decrease in the COIIIPIES- rod 85 moves upwardly and the tension of sion of the spring 29 nd by nfl fl the spring 78 is increased. Itwill, therethe fluid pressure beneath the piston 42 111- fore, be apparent that, with the apparatus cident to a restriction in the bleeding; and, h wn i 5, the tension 'of the back controlled ton 42 attains a position of equilibrium both from a distance. 1 by a decrease in the compression of the A clpser degree of'regulat on may be obspring 29 and a decrease in the'pressure betained by the use pf a spring 29 of finer neath the piston 42, the latter decreased scale; however, as this spring is weakened,.

pressure being obtained by anincreased' cathe stability of the'mechanism is decreased. pacity for bleeding incident to an increase in speed of the prime mover. speed variation from no load -to full load With a stronger spring, the percentage in i may be greater, but the stability of the 6 For example, if the tension of the spring 66 is' increased, this means that the piston valve member 61 is moved inwardly to restrict the ports 60 which, as already stated, results in the building up ofpressure beneath the piston 42 and the consequent opening of the admission valve 11 to a wider position. This results in an increase in the speed of the prime mover or turbine, and

the speed-responsive mechanism attains a condition ofequilibrium where the spring 66 and-the centrifugal force of the weight member 65 and the effect of the oil pressure on the piston 61 are balanced, with'a greater restriction of the ports 60. An increase in tension of the spring 66, therefore, results in a higher speed for the prime mover. A decrease in tension of this spring results in a contrary effect.

M improved governing mechanism preferab ggu'ses lubricating oil as an actuating fluid. I, therefore, show the outlet passageway 73 for the discharge chamber 33, the outlet passageway 7 5 for the space beneath the operating piston 24, the discharge conduit 103 for the discharge chamber 69, and

"the pressure-relief valve 20 for the pressure.- supply conduit 19, all communicating with the conduit 100, which is provided with connections 101 leading to the bearings 7 4 for the purpose of lubricating the latter. Surplus oil from the bearings is discharged into a passageway or conduit 102, which comnnunicates with the receiver or reservoir 18. It will, therefore, b seen that I have provided a combined governing and lubricating system in which oil issupplied at sufficient pressure from parts of the governing mechanism to secure adequate lubrication.

When starting up the prime mover, it is necessary to supply fluid tothe passageway- 19 "from some auxiliary source. Accordingly, I show, a passageway 105 adapted to be connected to any suitable source of fluid under pressure and which is controlled by means of a valve 106. In starting, fluid under pressure from the auxiliary source is admitted to the passageway 19, whereupon .such fluid enters the pressure chamber or passage 32 and then passes through the. restricted orifice connection 41, moving the piston 42 upwardly so that such fluid under pressure may be supplied to the operating piston 24 in order to move the latter downwardly for the purpose of opening'the admission valve 11. a The prime mover then starts, and thereafter the auxiliary source of fluid under pressure may be cut off and the pressure developed by the pump 13 solely relied upon.

It will be obvious to those skilled in that art that the fluid-pressure operated mechanism for the prime mover valve as well as the fluid-pressure controlling mechanism for the operated mechanism may be of any suitable type, or design, although the preferable type is the cylinder and piston kind. Also, while a spring is shown for closing the admission valve, it is to be understood that any device capable of producing the same result may be used.

While I have shown my invention in but two 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, and l desire, therefore, that only such limitations shall be placed there upon as are imposed by the prior art or as appended are specifically set forth in the claims.

. What I claim. is:

1. The combination witha prime mover having an admission valve, of governing mechanism for controlling the speed of the prime mover comprising a movable preslOU 2. In governing mechanism for controlling the supply of energy to a machine, the combination of energy-controlling mechanism including an element movable by fluid under pressure, a source of fluid under pressure, means for supplying fluid to said element from said source and for exhausting fluid from said element, amovable element connected to the last-named means, means for supplying fluid at'a lower average pres sure to one side of the last-named element, biasing means cooperating with said last named element to oppose movement thereof in response to fluid pressure, and means for relieving the pressure of fluid applied to said last-named element.

3. In governing mechanism for controllin'g the supply of energy to a machine, the combination. of energy-controlling mechanism includingan element movable byfluid under ressure in one direction, spring means for moving said mechanism, in the otherdirection, a source of fluid under'pressure, means for supplying fluid to said element from said source and for exhausting fluid from said element, a movable element connected to the last-named means, means for supplying fluid from said source at a lower average pressure to one side of the last-named element, biasing means cooperating with said last-named means and said element to oppose the fluid pressures, and means for relieving the pressure of ,fluid applied to said last-named element.

4. In governing mechanism for controlling the supply of energy to a machine, the

combination of energy-controlling mecha-' nism including an element movable in one direction by a fluid under pressure, a source of fluid under pressure, means for supplying fluid to said element from said source and for exhausting fluid from said element,

a movable element connected to the last named means, an orifice connection for sup- 7 plying, fluid from said source to one side of the last-named element, spring means cooperating with said moving elements and exerting its force thereupon in opposition to the fluid pressures applied thereto, and means for relieving the pressure of fluid applied to said last-named movable element in accordance with the speed'of the machine.

5. The combination with a steam motor having an admission valve, of governing mechanism for the motor comprising a movable abutment connected to the valve, a source of fluid under pressure, a valve for controlling the admission of fluid from said source to one side of the. abutment and the exhaust of such fluid therefrom, an abutment connected to the valve, a restricted orifice connection for supplying fluid to one side of the latter abutment from said source, speed-responsive means for relieving the fluid pressure on the latter abutment, and biasing means to secure movements of the abutments in directions opposite to movements thereof in response to fluid pressure whenever the force of the biasing means exceeds that of the fluid pressure.

6. The combination with a motor having an admission valve, of governing mechanism' for the motor comprising a movable abutment connected to the valve, a source of fluid under pressure, a valve for controlling the admission of fluid'from said source to the abutment and for controlling the exhaust of fluid therefrom, a movable abutment carried by the valve and normally subject to a pressure less than that of said source, speedresponsive means for relieving the pressure applied to the latter abutment, and spring means operative When the pressure on the latter abutment is relieved to move the valve to exhaust fluid from the first abutment and then to move the admission valve toward its closing position.

7. The combination with a motor having an admission valve, of governing mechanism for the motor comprising a spring for moving the valve in a closing direction, an operating piston for moving the valve in an opening direction and in opposition to the spring, a source of fluid under pressure,

a piston valve for controlling the admission of fluid from said source toone side of said: piston and the exhaust of fluid therefrom, an operating piston connected to the piston valve and subject to the pressure of said spring on one side and to the pressure of fluid on the otherside, and speed-responsive means for relieving the pressure of fluid applied to the latter operating piston.

speed-responsive means for controlling the relief of fluid pressure from said valve-operating piston so that the valvemay come toa neutral position under influence of the spring. 1 Y

9. The combination with a motor having an admission valve, means for developing fluid under pressure driven by said motor,

an operating piston connected to the admission valve, a valve for controlling the admission of fluid from said pressure-developing means'to one side of said operating piston and the exhaust of fluid therefrom, an

operating piston connected to the valve,

means for supplying fluid under pressure p to one side of the latter operating piston, a spring for exerting forces on said operating pistons in opposition to the fluid pressure forces applied thereto, and speed-responsive ineansfor relieving the pressure of fluid applied to the operating piston of the valve.

10. The combination with a motor having" an admissionvalve, of.governing mechanism for the motor comprising pressure-developing means driven by said motor,'an operating cylinder, an operating piston in the cylinder, a rod for connecting the piston to the admission valve, a piston valve for contro ling the admission of fluid from said pressure-developing means to said piston and the exhaust of fluid therefrom, a second operating cylinder in axial alinement with ing piston.

means, a spring under compression arranged between said rod and the second operating piston and exerting its force on the latter in opposition to fluid pressure, and speed-responsive means forrelieving pressure from the second operating piston.

" 11. The combination with a motor having an admission valve, of governing mechanism therefor comprising fluid pressure' developing means driven by the motor, an operating cylinder, an operating piston arranged within the cylinder, a rod for connecting the operating piston to the admission valve, a piston valve arranged coaxial with said rod for controlling' the admission of fluid from said pressure-developing means to one end of the operating cylinder and the exhaust of fluid therefrom, a second operating cylinder alined with the first cylinder, a second operating piston arrangedwithin the second operating cylinder and connected to the piston valve, means for-admitting fluid under pressure to one side ofithe second operating piston through a restricted orifice connection, a spring under compression arranged between said rod and the second opcrating piston and serving to oppose the fluid pressures applied to the pistons, and speed-responsive means for relieving the fluidpressure applied to 'the second operat- 12. The combination with a motor having an admission valve, of governing mechanism for the motor comprising fluid-pres; sure developing means driven thereby, an operating cylinder, an operating piston arranged within the cylinder and connected to the admission valve, a valve for controlling the admission of fluid from said pressure-developing means to one end of the operating cylinder and the exhaust of fluid therefrom, a second operating cylinder, a second operating piston arranged within the cylinder and connectedto the valve, a restricted orifice connection between the pressure-developing means and the second operating cylinder, :1. spring under compression for exerting its force against said opera-ting pistons in opposition to the fluid pressures 1 applied thereto, and speed-responsive means for relieving the pressure of fluid applied to the second operating piston.

13. The combination with a motor having an admission valve, of governing mechanism for the motor comprising pressure-developing means driven by the motor, an operating cylinder, an operating piston ar ranged within the cylinder, a rod for connectingthe piston to the admissionvalve, a slide valve for controlling the admission of pressure fromfluid from said fluid-pressure developing means to one end of the cylinder and the second operating piston, a spring under compression between the first and second oper ating pistons for normally opposing the fluid pressure-s applied thereto, and speedresponsive means for delivering the pressure of fluid applied to the second operating piston. I I

14; The combination with amotor having an admission. valve, of governing mechanism for 'the motor comprising fluid-pressure developing meansdriven by the motor, an operating cylinder, an operating piston within the cylinder, a piston rodfor con= necting the piston with the admissionvalve, a piston valve surrounding the piston rod and having slight clearance with respect thereto, a valve cylinder having passages communicating with said pressure-developing means and with the exhaust, means on the valve for placing the operating cylinder in communication with the pressure-developing means or with the exhaust dependent upon the valve position, a second operating piston connected to the valve, ports in the valve connecting the clearance'sp'ace with respect to the piston rod with said pressure-developing means and with the space at one side of the second operating p1ston a spring under compression and act- 4 mg on both pistons to oppose the fluid pressures applied thereto, and speed-responsive means for relieving the pressure of fluid applied to the second operating piston.

15. The combination with a prime mover having anadmission valve, of a spring for moving the valve in a closing direction, an

operating piston for moving the valve in an opening direction, fluid-pressure developing means driven by the prime mover, a valve for controlling the admission of fluid under said pressure-developing means to one side of the piston and'the exhaust of fluid therefrom, an operating piston connected to the valve, a restricted orifice connection between the pressure-developing means and one side of the second operating piston, adjustable pressure-relief means associated with the space at the other side of the second operating piston, and speed-responsive means for relieving the pressure of fluid applied .tothe first side of said second operating piston.

16. Thecombination with a prime mover having-an admission valve, of a spring for moving the valve in a closing direction, a fluid motor device for moving the valve in an opening direction and in opposition to the spring, a hollow shaft driven by the prime mover, a valve for one end of the shaft, speed-responsive means for controlling the opening and closure of said valve and rotating with the hollow shaft, and an exhaust connection between the motor device and the hollow shaft, whereby upon overspeeds of the prime mover, the rate of exhaust of fluid from thefluid motor is increased thereby permitting movement of the 10 admission valve in a closing direction due to the spring.

In testimony whereof, I have hereunto subscribed my name this 28th day ofDecember, 1922.

ALEXANDER T. KASLEY.

Images