US2009995A - Governor apparatus - Google Patents

Governor apparatus Download PDF

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Publication number
US2009995A
US2009995A US733630A US73363034A US2009995A US 2009995 A US2009995 A US 2009995A US 733630 A US733630 A US 733630A US 73363034 A US73363034 A US 73363034A US 2009995 A US2009995 A US 2009995A
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United States
Prior art keywords
governor
shaft
lever
casing
engine
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US733630A
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English (en)
Inventor
William F Engel
Otis D Treiber
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HERCULES MOTORS Corp
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HERCULES MOTORS CORP
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Priority to US733630A priority Critical patent/US2009995A/en
Priority to SE414634A priority patent/SE92950C1/sv
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D1/00—Controlling fuel-injection pumps, e.g. of high pressure injection type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D2700/00—Mechanical control of speed or power of a single cylinder piston engine
    • F02D2700/02—Controlling by changing the air or fuel supply
    • F02D2700/0269—Controlling by changing the air or fuel supply for air compressing engines with compression ignition
    • F02D2700/0282—Control of fuel supply
    • F02D2700/0284—Control of fuel supply by acting on the fuel pump control element
    • F02D2700/0292—Control of fuel supply by acting on the fuel pump control element depending on the speed of a centrifugal governor
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/0971—Speed responsive valve control
    • Y10T137/108—Centrifugal mass type [exclusive of liquid]

Definitions

  • the invention relates in general to governor apparatus adapted for association with means controlling the speed of rotation of a shaft, whereby regardless of the setting of the control 5 means the maximum speed of rotation of the shaft is maintained at a predetermined limit, and whereby a particular or idling speed of rotation of the shaft may be maintained automatically,
  • governor apparatus of the foregoing general character which is adapted for use in connection with a compression ignition internal combustion engine utilizing preferably liquid "hydrocarbon fuel such as Diesel 011, and used as the motive power for a vehicle such as a truck, bus, commercial car, passenger car, or the like.
  • the invention relates to governor apparatus of the foregoing general character and which in one form'is adapted for use in connection with a compression ignition internal combustion engine utilizing preferably liquid hydrocarbon fuel such as diesel oil and used as a variable torque controlled source of power for a power shovel, in which an increase in torque is desirable with increasing engine speeds up to a predeterminedintermediate engine speed which may be 900 R. P. M., after which the torque automatically falls oil at a predetermined rate with a further increase in the engine speed to a second intermediate engine speed, which may be 1300 R. P. M, and after which the torque very rapidly falls oil with further overrunning or increase in speed of the engine to the maximum speed.
  • a predeterminedintermediate engine speed which may be 900 R. P. M.
  • a second intermediate engine speed which may be 1300 R. P. M
  • the torque very rapidly falls oil with further overrunning or increase in speed of the engine to the maximum speed.
  • the objects of the present improvements include in general the provision of such governor apparatus in which the construction and arrangement of the parts of the governor apparatus is simplified so as to facilitate the manufacture and maintenance of the same.
  • governor apparatus of the foregoing description, and which includes simplified adjusting means for setting the apparatus with respect to the governor action both at the idling and maximum speeds, such adjusting means being externally accessible.
  • governor apparatus of the foregoing description which includes sim- 5 giglled and improved means for stopping the en-
  • Further objects of the present improvements include the provision of governor apparatus of the foregoing description, one form of which is 10 adapted for providing variable automatic torque control for a compression ignition internal combustion engine used as a source of power for a power shovel and the like.
  • the nature of the present invention may be described in general terms as including a rotary shaft, power drive means for the shaft, variable control means controlling the operation of the power drive means and adapted to be set to vary the speed of rotation of the shaft, control setting means operatively associated with the control means for varying the setting of the same, and governor means operatively-associated with the control setting means and with the control means and operative by governor action to maintain the speed of rotation of the shaft within predetermined limits with respect to an idling speed, and operative by governor action to limit the maximum speed of rotation of the shaft, the governor means including centrifugally actuated governor weights, externally accessible simplified means for adjusting the maximum speed at which the governor action takes place, and externally accessible simplified means for adjusting the idling speed governor action of the apparatus.
  • variable control setting means are provided, by which very accurate initial adjustments of the control setting means may be made.
  • the improved apparatus furthermore includes improved means for stopping the engine associated with parts of the improved adjustable means for setting the idling speed-of the engine.
  • the improved governor apparatus is preferably included in and/ or combined with a compression ignition internal combustion engine as is hereinafter set forth in greater detail, and the engine and apparatus also may include further novel improvements illustrated in the drawings and/or as hereinafter set forth.
  • FIG. 1 is a side elevation view of a compression ignition internal combustion engine having a fuel pump equipped with one embodiment of the improved governor apparatus of the present invention and being adapted for use as the motive power of a vehicle;
  • FIG. 2 an enlarged transverse sectional view of the improved governor apparatus, as on line 2-2, Fig. 1, distant parts of the engine and fuel pump, being removed;
  • Fig. 3 a fragmentary side elevation with portions broken away of the improved governor apparatus and portions of the fuel pump, distant parts of the engine being removed;
  • FIG. 4 an enlarged fragmentary longitudinal sectional view of the improved governor apparatus and portions of the fuel pump, distant parts of the engine being removed, as on line 44, Fig. 2; a
  • Fig. 5 a fragmentary elevation with portions broken away of the improved governor apparatus, illustrating the side thereof opposite to the side shown in Fig. 3, and showing the details of the improved stop means and parts of the variable adjusting means for the governor apparatus;
  • Fig. 6, a view similar to Fig. 4 illustrating another embodiment of the improved governor apparatusadapted for automatically providing a variable torque control for an engine used as a power source for a power shovel or the like.
  • a compression ignition internal combustion engine equipped with one embodiment of the present improved governor apparatus is indicated generally at It) in Figs. 1 to 5, inclusive, and as illustrated is a six cylinder, four strokecycle, single action, high speed, compression ignition internal combustion engine, in which the air'for combustion is obtained normally directly from the atmosphere, and in which separate quantities or charges of the preferred liquid hydrocarbon fuel, such as Diesel oil, are successively injected by-operation of a fuel pump indicated generally by H, into the combustion chambers of the engine at successive timed intervals, one charge being injected into the combustion chambers of each cylinder during each four stroke cycle of the piston operatively mounted in the cylinder.
  • a fuel pump indicated generally by H a fuel pump indicated generally by H
  • the fuel pump II is operatively mounted on one side of the engine as shown in Fig. 1, and as illustrated is of usual construction and arrangement and isa Bosch fuel injection pump, made by Robert Bosch, A. G., Stuttgart, Germany, and includes a shaft 12, driven by an operative connection with gearing contained in a gear housing l3 of the engine, the gears in the gear housing being driven by the engine crank shaft.
  • the gears and crank shaft are not shown, and may be of a usual construction and arrangement.
  • the fuel pump l I includes a casing H in which plunger pistons, not shown, are operatively mounted, each in a pump cylinder, not shown, formed in the casing I4, one pump plunger piston and cylinder being provided for each cylinder of the engine.
  • the plunger pistons are actuated in a usual manner by cams on a cam shaft portion, not shown, of the shaft l2, the cam shaft portion being located within a cam shaft chamber of the casing H.
  • Each pump cylinder communicates with a discharge outlet
  • the liquid fuel is supplied to the pump H through a main supply tube H in which an oil cleaner l8 may be interposed ahead of the fuel pump H.
  • the fuel pump is provided with the present improved governor apparatus indicated generally by l9, and the fuel pump also includes valve or variable metering means for each fuel pump cylinder controlling the quantity of liquid fuel admitted to each pump cylinder from the main supply tube and thus controlling the quantity of fuel in each charge pumped out of each pump cylinder into its associated engine cylinder combustion chambers on the pressure stroke of the piston of the pump cylinder.
  • the fuel pump l I furthermoreincludes a valve setting or throttle rod 20 which is operatively associated with each of the valve means for each of the pump cylinders and which is arranged for reciprocation in normally horizontal opposite directions in the casing H of the fuel pump II.
  • the rod 20 when displaced to its extreme po-' sition in the direction of the arrow S, in Figs. 3 and 4 actuates the valve means so as to shut off the flow of liquid fuel into the pump cylinders, and thus stops the engine.
  • the pump valve means are set to a position for permitting a flow of fuel into the pump cylinders at such rate as to cause the engine It) to operate at a desired idling speed.
  • Displacement of the rod 20 in the direction of the arrow F actuates the pump valve means to increase the rate of flow of liquid fuel into the pump cylinders, the greater the displacement of the rod 20 in the direction of the arrow F, the greater the rate of flow of liquid fuel into the pump cylinders.
  • valve means of the pump cyling the speed of operation of the engine, and the rod 22 may be termed a control means actuating member which is movable between two extreme positions, one of which is such that the control means are actuated to stop the engine or apparatus controlled by the control or valve means, and the other of which is such that the control means are actuated so as to run the engine at full speed. and intermediate positions of which include a setting which provides an idling speed for the engine, and provides for varying speeds thereof between the idling speed and the full speed.
  • the governor apparatus i9 preferably includes a casing indicated generally by 2
  • the governor casing section 22' includes an end wall 24 which abuts against the adjacent end wall 25 of the pump casing l4, and the governor drive end 29 of the pump shaft
  • a governor drive gear 22 is secured upon the govemor drive end 22 of the pump shaft l2 within the governor chamber 22, and also within the governor chamber, a governor shaft 29 is journal mounted at opposite ends as by means of antifriction bearing means indicated generally by 22 and 2
  • the longitudinal axis of rotation of the governor shaft 29 is preferably parallel with the longitudinal axis of rotation of the pump shaft l2 and the governor shaft has secured thereon a driven pinion 22 which is located adjacent the anti-friction bearing means 20 and which is meshed with the governor drive gear 22, whereby rotation of the pump shaft l2 driven as aforesaid frcm the crank shaft of the engine, serves to rotate the governor shaft 22'.
  • the governor shaft 29 has secured thereon, in the illustrated embodiment adjacent the driven pinion 22, a spider 24 having sets of arms 29 and '29 respectively extending from diametrically opposite sides of the shaft 29, and governor weights 29 and 29' are pivotally mounted intermediate their ends respectively on the opposite sets of spider arms 25 and 25', as by means of spider pins 21 and 21, the longitudinal axes of which are parallel, and which are spaced at equal distances from the longitudinal axis of the governor shaft 29, and lie in a plane normal to the longitudinal axis of the shaft 29.
  • the governor weights 29 and 29? are of a desired shape, and are substantially identical with each other, and have their centers of gravity located at equal distances from the longitudinal axes of the pins 91 and 31"beyond the outer extremities of the sets of spider arms 22 and 25'.
  • Thegovernor weights 26 and 29' include respectively sleeve actuating tongues 22 and 22' which extend toward the governor shaft 29, the
  • control means determinspider pins 21 and 21 and the governor shaft 22.
  • the governor weights 22 and 22 also include at their inner extremities stop tongues 22 and 22' which abut against opposite stop faces on the spider hub 42 and limit the outward movement of the weights 22 and 22' under the action of the centrifugal forces set up therein by rotation of the shaft 22.
  • is slidably mounted on the governor shaft 22 between the spider 24 and the outer bearing means 2
  • adjacent the tongues 22 and 22' of the governor weights 22 and 22' is abuttable by the outer extremities of the tongues 22 and 22', and the sleeve 4
  • the governor apparatus 9 furthermore includes a yoke lever pivoting eccentric shaft 42 which is journalled at its ends in the opposite side walls 42 and 41 of the governor casing section 22, and which is located at one side of, and
  • a yoke lever 42 is pivotally mounted at one end 49 on the eccentric shaft 42, and the yoke lever end 42 as illustrated is the lower end of the yoke lever 42.
  • the yoke lever 42 has formed therein a central 7 opening 22, and the governor shaft 29, the sleeve 4
  • the yoke lever 42 includes side members 2
  • the ring 42 has formed in its outer peripheral surface an outwardly opening annular groove 22 and pins 22 and 22' have their outer ends respectively secured in the yokev side members II and Ii and have their inner ends extending into the ring groove 22.
  • a connector ear I4 is provided and a longitudinally adjustable link means is pivotally connected at its outer end with the ear 24, as by pin means 22, and the link means 29 is pivotally connected at its inner end with the outer extremity of the rod 22 as by pin means 21.
  • a compression spring 12 is interposed betweenthe upper end of the yoke lever 42, and an externally threaded adjustable screw plug 1
  • for the governor shaft 29 is carried in externally accessible means indicated generally by 12 for adjusting and determining the maximum speed at which governor action takes place, as aforesaid.
  • the maximum speed governor action adjuste ing means 12 includes a tubular member 19, which is preferably externally cylindric in its central portions and whose externally cylindric central portions fit in a cylindric bore formed in the governor casing end wall 32, the ends of the tubular member I3 extending beyond opposite sides of the casing end wall 32, and the inner end of the tubular member 13 being provided within the governor chamber 22 with an inwardly extending annular flange 14.
  • the tubular member 13 on the outside of the casing wall 32 is provided with an'outwarclly extending annular flange 15, and initial clearance shims 16 are interposed between the flange 18 and the wall 32.
  • the outer end ll of the tubular member I3 extends outwardly beyond the flange IS.
  • a bearing and adjusting means mounting cap 18 is mounted on the outer end 11 of the tubular member I3.
  • the cap 78 is provided with an internal socket 80 formed to seat at its outer end the outer raceway member 3
  • the cap socket 80 has rotatably mounted therein in rotary abutment with the inner side of the outer raceway member 3
  • the socket 88 includes an enlarged inner end portion or counterbore 84 which fits on the outer end ll of the tubular member 13, and the outer extremity of the tubular member 13 terminates intermediate the ends of the enlarged portion 84 of the cap 18, and a spring seat member 88 is located in the counterbore 84 between the ring 8
  • the spring seat member 88 includes a central sleeve hub 81 through the bore of which the shaft 29 passes and which extends into the bore 88 of the ring 8
  • a tongue and notch connection thereof with the outer end ll of the tubular member I3 is provided, as illustrated by tongues -88
  • the cap 18 has journal mounted therein a worm screw 89 having a screw head 90 located externally of the cap 18, and the worm screw 89 is meshed with the worm threads 82 formed externally in the ring 8 I, and accordingly rotation of the worm screw 89 serves to turn the ring 8 I, and the spring seat 86 screw connected with the ring 8
  • extends through the opening of the annular flange ll of the tubular member 19, and the reacting ring 9
  • is provided on its end within the governor chamber 22 with an inwardly extending annular flange 93 and a compression spring 94 is interposed between the spring seat member 86 and the inwardly extending annular flange 93 of the reacting ring 9
  • the cap 18 as illustrated is provided at its inner end with a flange 95 and a gasket 98 is preferably interposed between the flange 95 and the flange 15 of the tubular member 73, and screws 91 preferably secure and seal the flange 95 to the flange 15 .whereby the maximum speed governor action adjusting means 12 above described including the tubular member I3, the cap E8 and the parts operatively mounted therein, may be preassembled as a unit and may be easily inserted upon or removed from the outer end of the shaft 29.
  • Cap screws 98 are provided as shown for securing the unitary maximum speed governor action adjusting means 12 to the wall 32.
  • the eccentric shaft 45 includes an eccentric portion 45a on which the yoke lever end 49 is pivotally or rotatably mounted as aforesaid, and the eccentric shaft, furthermore includes axially alined end journal portions 451) and 450 which are rotatably mounted respectively in the governor casing side walls 48 and 41, and the journal portion 95b of the eccentric shaft 45 extends beyond the outer side of the casing side wall 41 and has secured thereon externally of the governor casing 2
  • the maximum speed governor action adjusting means 12 is provided with an initial clearance by means of the shims I6, whereby the outer face of the flange'93 is normally spaced a slight distance from the antifriction bearing 44, and the tendency of the governor weights 36 and 36' to move the sleeve 4
  • the eccentric shaft is mounted in the casing side walls 40 and 41, by providing in each of the opposite side walls 40 and 41 aligned of flow of fuelbores I02 and I05, respectively, the diameters of the bores I02 and I 03 being large enough to permit the endwise insertion and removal there.- through of the eccentric shaft 45.
  • the bore I02 of the wall 40 has removably secured therein a bearing and bracket plug I04 which has a bearingbore iournalling the eccentric shaft Journal portion 45c; and the bore I02 in.the wall 41 has removably secured therein a bearing plug I05 which has a bearing bore there- 11; 3011 the eccentric shaft Journal porti
  • the control setting lever 09-2 is preferably ad-' Justably secured on the external end of the shaft portion 45b as best shown in Figs.
  • worm screw and worm wheel means indicated generally by I00 and which include a worm wheel I01 secured on the shaft portion 45b and the worm wheel III is engirdled-by a split rlng hub I00 provided on the lever 00-2 and a worm screw III is iournalled and extends through opposite split portions III and III of the hub and the threads of the screw I05 are meshed with the threads of the worm wheel I01, whereby rotation of the worm screw enables adjustment of the position of the arm -2, to the proper position with respect to the mechanism of the apparatus within the'casing 2I and with respect to the external connections to the accelerator pedal or like control for the en ine.
  • the outer screw end of the worm screw I00 preferably is provided with a lock or clamping nut II2.
  • a maximum speed stop pin IIO. is secured on a plate II4 interposed between the hub I00 and the plug I05 and secured to the plug I05-and the hub I00 has a maximum speed stop tongue II5 extending therefrom and adapted to stop abut against the pin II3.
  • the end of the plug I05 is notched to form a stop face IIG adapted to be abutted by a pin I I1 extending from the opposite end of the eccentric portion 45a to limit motion of the eccentric in the direction causing a shut! ting off of the fuel supply.
  • the plug and bracket I04 as best shown in Fig. 5 is secured to the outer side of the casing wall 40 and the eccentric shaft portion 45c extends beyond the outer face of the plug and bracket I04 and has associated therewith preferably adjustable idling speed setting and engine stop means indicated generally by IIO which prevents rotation of the shaft 45 in the fuel shutting of! direction normally beyond a position permitting governor controlled,
  • the idling speed setting and engine stop means III preferably include a single tooth ratchet split ring I I0 engirdling a worm wheel I20 which is mined on the shaft end portion 450, and a worm screw I2I' extends through aligned. bores in op-- posite split ends I22 and I23 of the ring 9, and the threads of the screw I2I are meshed with the threads of the worm wheel I 20 whereby minute adjustment of the position of the tooth I 24 of the ratchet ring 0 with respect to the shaft 45 and the other parts of the apparatus within the casing H is attained.
  • a hook pawl I25 is pivotally mounted on the bracket I04 and the hook pawl I 25 includes a stop hook end I26 which is urged towards the shaft 450 by spring means I21 and provides a releasable idling speed stop adapted to impinge the ratchet tooth I24 and prevent further rotation of the coitigentric shaft 45 beyond the idling speed setting reof.
  • the pawl I25 For permitting stopping of the engine, the pawl I25 includes a release arm I29 which as illustrated is connected as by a wire I29 with the dash board or the like of the vehicle or other apparatus with which the governor means I9 is associated, and by pulling the wire I29, the pawl stop hook end I23 is released for engagement from the tooth I24 permitting further rotation of the shaft 45 in.
  • Fig. 6a modified embodiment I3 of the improved governor apparatus is illustrated, and the governor apparatus I9 is adapted for a variable torque control of a Diesel engine, such as the engine I0 when used as a power supply for a power shovel.
  • the parts of the governor apparatus I9, as illustrated are identical with the parts of the apparatus I9 heretofore described, with the'following exceptions.
  • the spring 94 is not utilized and there is interposed between the reaction member 9
  • the member I30 also includes an outwardly extending annular stop and spring seat flange I33 which is opposite the spring seat member 86 and which normally abuts against a shoulder I34 formed in the end of the tubular member 13 ad jacent the shoulder flange 14.
  • a compression spring I35 is interposed between and reacts against the adjustable spring seat member 86 and the flange I33 of the intermediate member I30, and another compression spring I36 is interposed between the reacting member flange 93 and the flange I32 of the intermediate mem- 'ber I30.
  • the resistance or loading of the springs I 35 and I36 are different from each other, the spring I33 having the least initial load, and the rate of deflection however of the spring I35 is greater than the rate of deflection of the spring I38.
  • the reacting member 9I abuts against the intermediate member I30 and the force tending to move the sleeve 4I may then have attained such magnitude as to rapidly compress the spring I35 and rapidly shut off the supply of fuel to the engine until if desired the entire fuel supply is shut oif.
  • the normal shovel speed may be 1300 'R. P. M., and accordingly when the shovel engine tion of the rotary shaft driven thereby, control setting means operatively associated with the applying a force in the opposite direction against the lever, the lever adjacent one end thereof having an operative connection with the variable control means, and the control setting means including a crank pivotally mounting the lever adjacent the other end thereof, and the resilient means being loaded so as to prevent movement of the lever by the action of the centrifugally induced force of the governor means during a normal speed range of the rotary shaft.
  • governor controlled apparatus including a rotary shaft, power drive means for the shaft, variable control means controlling the operation of the power drive means and the speed of rotation of the rotary shaft driven thereby, control setting means operatively associated with the control means for varying the setting of the same, and governor means operatively associated with the power drive means and with the control means and with the control setting means, the governor means including a lever operating the variable control means and operated by the control setting means, centrifugally operating means pivotally and slidably associated with the lever intermediate its ends and connected for rotation by the shaft and adapted to apply a force in one direction against the lever, and adjustable resilient means applying a force in the opposite direction against the lever, the lever adjacent one end thereof having an operative connection with the variable control means, and the control setting means including a crank pivotally mounting the lever adjacent the other end thereof, and the resilient means being loaded so as to prevent movement of the lever by the action of the centrifugally induced force of the governor means during a normal speed range of the rotary shaft.
  • governor controlled apparatus including a rotary shaft, power drive means for the shaft, variable control means controlling the operation of the power drive means and the speed of rotation of the rotary shaft driven thereby, control setting means operatively associated with the control means for varying the setting of the same, and governor means operatively associated with the power drive means and with the control means and with the control setting means, the governor means including a lever operating the variable control means and operated by the control setting means, centrifugally operating means pivotally and slidably associated with the lever intermediate its ends and connected for rotation by the shaft and adapted to apply a force in one direction against the lever, and resilient means including a spring pressed reacting member located at the side of the lever opposite the direction of the centrifugally applied force, and the spring pressed reacting member being adapted to be abutted by the lever and resist movement thereof by the action of the centrifugally applied force, the lever adjacent one end thereof having an operative connection with the variable rotary shaft, power drive means for the shaft,
  • variable control means controlling the operation of the power drive means and the speed of rotation of the rotary shaft driven thereby, control setting means operatively associated with the control means for varying the setting of the same, and governor means operatively associated with the power drive means and with the control means and with the control setting means, the governor means including a lever operating the variable control means andoperated by the control setting means, centrifugally operating means pivotally and slidably associated with the lever intermediate its ends and connected'for rotation by the shaft and adapted to apply a force in one direction against the lever, and resilient means including an adjustable spring pressed reacting member located at the side of the lever opposite the direction of the centrifugally applied force, and the spring pressed reacting member being adapted to be abutted by the lever and resist movement thereof by the action of the centrifugally applied force, the lever adjacent one end thereof having an operative connection with the variable control means, and the control setting means including a crank pivotally mounting the lever adjacent the other endthereof, and the resilient means being loaded so as to prevent movement of the lever by the
  • governor controlled apparatus including a rotary shaft, power drive means for the shaft, variable control means controlling the operation of the power drive means and the speed of rotation of the rotary shaft driven thereby, control setting means operatively associated with the control means for varying the setting of the same, and governor means operatively associated with the power drive means andwith the control means and with the control setting means, the governor means including a lever operating the variable control means and operated by the control setting means, centrifugaliy operating means pivotally and slidably associated with the lever intermediate its ends and connected for rotation by the shaft and adapted to apply a force in one direction against the lever, and resilient means including a spring pressed reacting member located at the side of the lever opposite the direction of the centrifugally ap l ed force, and the spring pressed.
  • reacting member being adapted to be abutted by the lever and resist movement thereof by the action of the centrifugally applied force
  • resilient means adapted to apply a second force upon the lever in the opposite direction to the centrifugally applied foran'the lever adjacent one end thereof having an operative connection with the variable control means
  • control setting means including a crank pivotally mounting the lever adjacent the other end thereof, and the resilient means being loaded o as to prevent movement of the lever by the action of the centrifugally induced force of the governor means during a normal speed range of the rotary shaft.
  • adjustable resilient reacting means including a longitudinally extending mounting member having a stop flange at one end, a reacting member mounted for longitudinal movement with respect to the mounting member, the reacting member hav-' ing a flange normally abutting against the mounting member stop flange, a ,spring seat member, means adiustably mounting the spring seat member on the mounting member with the reacting member located between the mounting member stop flange and the spring seat member,
  • thespring seat member mounting means including a rotary member operatively associated with the spring seat member whereby rotation of the rotary member moves the spring seat member longitudinally for varying the loading of the spring, the rotary member having worm wheel I threads thereon and a worm screw operatively associated with the worm wheel threads for turning the rotary member.
  • unitary adjustable resilient reacting means including a longitudinally extending tubular mounting member having a stop flange at one end, 'a reacting member mounted for longitudinal movement with respect to the tubular member, the reacting member having a flange within the bore of the tubular member and normally abutting against the tubular member stop flange, a cap secured on the other end of the tubular member, the cap having a longitudinally extending socket formed therein and comprising a longitudinal extension of the bore of the tubular member, a spring seat member located "within the socket, a compression spring interposed between the reacting member and the spring seat member, a rotary member rotatably mounted in the socket and operatively associated with the spring seat member whereby rotation of the rotary member moves the spring seat member longitudinally for varying the loading of the spring, the rotary member having worm wheel threads thereon, a worm screw rotatably mounted in the cap and operatively associated with the worm wheel threads, and the worm screw having a
  • a casing operatively mounted within the casing, means for varying the setting of the valve setting means including a shaft operatively associated with the valve setting means within the casing, the shaft extending externally of the casing, a control lever, and means adiustably mounting the control lever on the shaft outside of the casing, the means adjustably mounting the control lever on the shaft including interacting members on the lever and the shaft adapted for operation to vary and set the angular position of the lever with respect to an element of the shaft.
  • a casing operatively mounted within the casing, a shaft operatively associated with the valve setting means within the casing, the shaft extending externally of the casing, the shaft being adapted for manual rotation outside of the casing for varying the setting of the valve setting means within the casing, means outside of the casing for releasably stopping rotation of the shaft in one direction beyond a position establishing an in termediate governor controlled setting of the valve setting means within the casing.
  • a casing operatively mounted within the casing, a shaft operatively associated with the valve setting means within the casing, the shaft extending externally of the casing, the shaft being adapted for manual rotation outside of the casing ior varying the setting of the valve setting means within the casing, means outside of the easing for releasably stopping rotation of the shaft in one direction beyond a position establishing an intermediate governor controlled setting of the valve setting means withinthe casing, and means for manually releasing the releasable stop means from stopping relationship with the shaft.
  • a casing, governor controlled valve setting means operatively mounted within the casing; a shaft operatively associated with the valve setting means within the casing, the shaft extending externally of the casing, the shaft being adapted for manual rotation outside of the casing for varying the setting of the valve setting means within the casing, means outside of the casing for releasably stopping rotation of the shaft in one direction beyond a position establishing an intermediate governor controlled setting of the valve setting means within the casing, the releasable stop means including a ratchet secured on the shaft, the ratchet having a single stop tooth, and a pawl associated with the ratchet and normally maintained in position for engaging the ratchet stop tooth.
  • a casing governor controlled valve setting means operatively mounted within the casing, a shaft operatively associated with the valve setting means within thecasing, the shaft extending externally of the casing, the shaft being adapted for manual rotation outside of the casing for varying the setting of the valve setting means within the casing, means outside of the casing for releasably stopping rotation of the shaft in one direction beyond a position establishing an intermediate governor controlled setting of the valve setting means within the casing, the releasable stop means including a ratchet secured on the shaft, the ratchet having a single stop tooth, and
  • resilient reacting means including a longitudinally extending mounting member having a stop flange at one end, a reacting member mounted for longitudinal movement with respect to the mounting member, the reacting member having a flange normally abutting against the mounting member stop flange, a first spring seat member mounted on the mounting member with the reacting member located between the mounting member stop flange and the first spring seat member, an intermediate spring seat member located between the reacting member and the first spring seat member, a first compression spring interposed between the first spring seat member and the intermediate spring seat member and a second compression spring interposed between the intermediate spring seat member and the reacting member.
  • resilient reacting means including a longitudinally extending mounting member having a stop flange at one end, a reacting member mounted for longitudinal movement with respect to the mounting member, the reacting member having a flange normally abutting against the mounting member stop flange, a first spring seat member mounted on the mounting member with the reacting member located between the mounting member stop flange and the first spring seat member, an intermediate spring seat member located between the reacting member and the first spring seat member, a first compression spring interposed between the firstspring seat member and the intermediate spring seat member and a second compression spring interposed between the intermediate spring seat member and the reacting member, the springs having diiferent rates of deflection.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • High-Pressure Fuel Injection Pump Control (AREA)
US733630A 1934-07-03 1934-07-03 Governor apparatus Expired - Lifetime US2009995A (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
US733630A US2009995A (en) 1934-07-03 1934-07-03 Governor apparatus
SE414634A SE92950C1 (en, 2012) 1934-07-03 1934-10-19

Applications Claiming Priority (1)

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Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2457748A (en) * 1944-02-22 1948-12-28 Gen Railway Signal Co Speed governor for railway, vehicles
US2511095A (en) * 1947-02-01 1950-06-13 Caterpillar Tractor Co Engine governor
US2631025A (en) * 1948-09-30 1953-03-10 Westinghouse Air Brake Co Successively operated speeder springs for speed governors
US2668455A (en) * 1949-11-23 1954-02-09 Krupp F Lokomotivfabrik Remote control mechanism, especially for vehicles with fluid drive
US2739802A (en) * 1949-08-26 1956-03-27 Waukesha Motor Co Engine governor utilizing plural rate spring
US2865347A (en) * 1954-09-23 1958-12-23 Vernon D Roosa Control means for a fuel pump valve
US2908265A (en) * 1957-01-09 1959-10-13 List Hans Governor
US2988922A (en) * 1955-10-07 1961-06-20 Porsche Kg Centrifugal governor for internal combustion engines
US3451405A (en) * 1967-06-19 1969-06-24 Caterpillar Tractor Co Centrifugal flyweight engine governor
FR2512113A1 (fr) * 1981-08-27 1983-03-04 Spica Spa Regulateur de regime pour pompes a injection de combustible

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2457748A (en) * 1944-02-22 1948-12-28 Gen Railway Signal Co Speed governor for railway, vehicles
US2511095A (en) * 1947-02-01 1950-06-13 Caterpillar Tractor Co Engine governor
US2631025A (en) * 1948-09-30 1953-03-10 Westinghouse Air Brake Co Successively operated speeder springs for speed governors
US2739802A (en) * 1949-08-26 1956-03-27 Waukesha Motor Co Engine governor utilizing plural rate spring
US2668455A (en) * 1949-11-23 1954-02-09 Krupp F Lokomotivfabrik Remote control mechanism, especially for vehicles with fluid drive
US2865347A (en) * 1954-09-23 1958-12-23 Vernon D Roosa Control means for a fuel pump valve
US2988922A (en) * 1955-10-07 1961-06-20 Porsche Kg Centrifugal governor for internal combustion engines
US2908265A (en) * 1957-01-09 1959-10-13 List Hans Governor
US3451405A (en) * 1967-06-19 1969-06-24 Caterpillar Tractor Co Centrifugal flyweight engine governor
FR2512113A1 (fr) * 1981-08-27 1983-03-04 Spica Spa Regulateur de regime pour pompes a injection de combustible

Also Published As

Publication number Publication date
SE92950C1 (en, 2012) 1938-10-14

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